Refrigeration apparatus

ABSTRACT

A refrigeration apparatus includes a compression mechanism, a heat source-side heat exchanger, a usage-side heat exchanger, a switching mechanism and an intermediate heat exchanger. Refrigerant discharged from a first-stage compression element is sequentially compressed by a second-stage compression element. Each of the heat source-side heat exchanger and the usage-side heat exchanger functions an evaporator or radiator. The switching mechanism is configured to switch between a cooling operation state and a heating operation state. The intermediate heat exchanger is configured to cool refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element when the switching mechanism has been set to the cooling operation state, and to evaporate refrigerant whose heat is radiated in the usage-side heat exchanger when the switching mechanism has been set to the heating operation state.

TECHNICAL FIELD

The present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus which has a refrigerant circuit configured to be capable of switching between a cooling operation and a heating operation and which performs a multistage compression refrigeration cycle.

BACKGROUND ART

As one conventional example of a refrigeration apparatus which has a refrigerant circuit configured to be capable of switching between a cooling operation and a heating operation and which performs a multistage compression refrigeration cycle, there is disclosed in Patent Document 1 an air-conditioning apparatus which has a refrigerant circuit configured to be capable of switching between an air-cooling operation and an air-warming operation and which performs a two-stage compression refrigeration cycle. This air-conditioning apparatus primarily has a compressor having two compression elements connected in series, a four-way switching valve for switching between an air-cooling operation and an air-warming operation, an outdoor heat exchanger, and an indoor heat exchanger.

<Patent Document 1>

Japanese Laid-open Patent Application No. 2007-232263

DISCLOSURE OF THE INVENTION

A refrigeration apparatus according to a first aspect of the present invention comprises a compression mechanism, a heat source-side heat exchanger which functions as a radiator or evaporator of refrigerant, a usage-side heat exchanger which functions as an evaporator or radiator of refrigerant, a switching mechanism, and an intermediate heat exchanger. The compression mechanism has a plurality of compression elements and is configured so that the refrigerant discharged from the first-stage compression element, which is one of a plurality of compression elements, is sequentially compressed by the second-stage compression element. As used herein, the term “compression mechanism” refers to a compressor in which a plurality of compression elements are integrally incorporated, or a configuration that includes a compressor in which a single compression element is incorporated and/or a plurality of compressor in which a plurality of compression elements have been incorporated are connected together. The phrase “the refrigerant discharged from a first-stage compression element, which is one of the plurality of compression elements, is sequentially compressed by a second-stage compression element” does not mean merely that two compression elements connected in series are included, namely, the “first-stage compression element” and the “second-stage compression element,” but that a plurality of compression elements are connected in series and the relationship between the compression elements is the same as the relationship between the aforementioned “first-stage compression element” and “second-stage compression element.” The switching mechanism is a mechanism for switching between a cooling operation state wherein refrigerant is circulated sequentially through the compression mechanism, the heat source-side heat exchanger functioning as a refrigerant radiator, and the usage-side heat exchanger functioning as an evaporator of refrigerant; and a heating operation state wherein refrigerant is circulated sequentially through the compression mechanism, the usage-side heat exchanger functioning as a refrigerant radiator, and the heat source-side heat exchanger functioning as an evaporator of refrigerant. The intermediate heat exchanger is a heat exchanger capable of functioning as a cooler of refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element when the switching mechanism has been set to the cooling operation state, and also capable of functioning as an evaporator of refrigerant whose heat is radiated in the usage-side heat exchanger when the switching mechanism has been set to the heating operation state.

In a conventional air-conditioning apparatus, since the refrigerant discharged from a first stage compression element of the compressor is drawn into a second-stage compression element of the compressor and further compressed, the temperature of the refrigerant discharged from the second-stage compression element of the compressor increases. In an outdoor heat exchanger functioning as a refrigerant radiator, for example, the temperature difference between the refrigerant and the water and/or air as a heating source increases, and heat radiation loss in the outdoor heat exchanger increases, therefore causing a problem in that high operation efficiency is difficult to obtain.

As a countermeasure to this problem, in cases in which an intermediate heat exchanger is provided which functions as a cooler of refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element, such as is the case with this refrigeration apparatus, the temperature of the refrigerant drawn into the second-stage compression element is lower, and the temperature of the refrigerant ultimately discharged from the compression mechanism can therefore be kept low in comparison with cases in which no intermediate heat exchanger is provided. Operation efficiency can therefore be improved during the cooling operation because heat radiation loss during the cooling operation can be reduced in the heat source-side heat exchanger which functions as a refrigerant radiator.

However, since an intermediate heat exchanger is provided, the heat that would have been useable in the usage-side heat exchanger during the heating operation if there were no intermediate heat exchanger functioning as a cooler of refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element during the heating operation is radiated to the exterior from the intermediate heat exchanger, whereby the heating capacity in the usage-side heat exchanger decreases, and the operation efficiency during the heating operation decreases.

As a countermeasure to this, for example, an intermediate heat exchanger bypass tube for bypassing the intermediate heat exchanger is provided, and during the heating operation the intermediate heat exchanger bypass tube is used so that the refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element bypasses the intermediate heat exchanger so as not to be cooled, thereby creating a state in which the intermediate heat exchanger is not used, whereby the loss of heating capacity in the usage-side heat exchanger is minimized during the heating operation, and operation efficiency during the heating operation can be prevented from decreasing.

However, when a state is created in which the intermediate heat exchanger is not used during the heating operation, the intermediate heat exchanger is provided as a heat exchanger used only during the cooling operation, and the intermediate heat exchanger will therefore be a device not used during the heating operation.

In view of this, in this refrigeration apparatus, the intermediate heat exchanger is made to function as a cooler when the switching mechanism has been set to the cooling operation state, and when the switching mechanism has been set to the heating operation state, the intermediate heat exchanger is made to function as an evaporator of refrigerant whose heat is radiated in the usage-side heat exchanger. Therefore, in this refrigeration apparatus, the temperature of the refrigerant discharged from the compression mechanism can be minimized during the cooling operation, and during the heating operation, the refrigerant evaporation capacity can be improved while the heat radiated to the exterior from the intermediate heat exchanger can be minimized.

Thereby, in this refrigeration apparatus, during the cooling operation, heat radiation loss in the heat source-side heat exchanger functioning as a refrigerant radiator is reduced, and the operation efficiency during the cooling operation can be improved, while during the heating operation, it is possible to efficiently use the intermediate heat exchanger, loss of heating capacity in the usage-side heat exchanger can be minimized, and the operation efficiency during the heating operation can be prevented from decreasing.

The refrigeration apparatus according to a second aspect of the present invention is the refrigeration apparatus according to the first aspect, wherein the intermediate heat exchanger is provided with an intermediate refrigerant tube for drawing the refrigerant discharged from the first-stage compression element into the second-stage compression element, an intermediate heat exchanger bypass tube is connected to the intermediate refrigerant tube so as to bypass the intermediate heat exchanger; and the refrigeration apparatus further comprises an intake return tube for connecting one end of the intermediate heat exchanger with an intake side of the compression mechanism, and an intermediate heat exchanger return tube for connecting the other end of the intermediate heat exchanger with the portion between the usage-side heat exchanger and the heat source-side heat exchanger.

In this refrigeration apparatus, the intermediate-pressure refrigerant flowing through the intermediate refrigerant tube can be cooled by the intermediate heat exchanger during the cooling operation, and during the heating operation, the intermediate-pressure refrigerant flowing through the intermediate refrigerant tube is made to bypass the intermediate heat exchanger by the intermediate heat exchanger bypass tube, and some of the refrigerant cooled in the usage-side heat exchanger can be drawn into and evaporated in the intermediate heat exchanger and can be returned to the intake side of the compression mechanism by the intake return tube and the intermediate heat exchanger return tube.

The refrigeration apparatus according to a third aspect of the present invention is the refrigeration apparatus according to the second aspect, wherein at the start of the operation for setting the switching mechanism to the cooling operation state, the refrigerant discharged from the first-stage compression element is drawn into the second-stage compression element through the intermediate heat exchanger bypass tube, and the intermediate heat exchanger is connected with the intake side of the compression mechanism through the intake return tube.

In this refrigeration apparatus, at the start of the operation for setting the switching mechanism to the cooling operation state, since the refrigerant discharged from the first-stage compression element is drawn into the second-stage compression element through the intermediate heat exchanger bypass tube and the intermediate heat exchanger is connected with the intake side of the compression mechanism through the intake return tube, even if liquid refrigerant accumulates in the intermediate heat exchanger at the start of the operation for setting the switching mechanism to the cooling operation state, this liquid refrigerant can be removed from the intermediate heat exchanger. Thereby, at the start of the operation for setting the switching mechanism to the cooling operation state, it is possible to avoid states in which liquid refrigerant has accumulated in the intermediate heat exchanger, and the refrigerant discharged from the first-stage compression element can be drawn into the second-stage compression element through the intermediate heat exchanger without any liquid compression occurring in the second-stage compression element as a result of liquid refrigerant accumulating in the intermediate heat exchanger.

The refrigeration apparatus according to a fourth aspect of the present invention is the refrigeration apparatus according to the second or third aspect, wherein the intermediate heat exchanger return tube is provided with a flow rate control valve.

In this refrigeration apparatus, refrigerant can be prevented from flowing into the intermediate heat exchanger return tube during the cooling operation, and it is possible to achieve a reliable distribution between the flow rate of the refrigerant flowing through the heat source-side heat exchanger and the flow rate of the refrigerant flowing through the intermediate heat exchanger during the heating operation.

The refrigeration apparatus according to a fifth aspect of the present invention is the refrigeration apparatus according to any of the first through fourth aspects, wherein an expansion device for isentropically expanding the refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger is connected to the portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit which rectifies the refrigerant flow so that refrigerant flows in from the inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.

In this refrigeration apparatus, it is possible to improve the coefficient of performance and to recover energy through the expansion device during both the cooling operation and the heating operation, and operation efficiency during both the cooling operation and the heating operation can therefore be further improved.

The refrigeration apparatus according to a sixth aspect of the present invention is the refrigeration apparatus according to the fifth aspect, wherein a gas-liquid separator for performing gas-liquid separation of the refrigerant is connected to an outlet of the expansion device, and a second-stage injection tube for returning to the second-stage compression element gas refrigerant separated in the gas-liquid separator is connected to the gas-liquid separator.

In this refrigeration apparatus, operation efficiency can be further improved because intermediate pressure injection can be performed for returning intermediate-pressure refrigerant to the second-stage compression element.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic structural diagram of an air-conditioning apparatus as an embodiment of the refrigeration apparatus according to the present invention.

FIG. 2 is a diagram showing the flow of refrigerant within the air-conditioning apparatus during the air-cooling operation.

FIG. 3 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation.

FIG. 4 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation.

FIG. 5 is a diagram showing the flow of refrigerant within the air-conditioning apparatus during the air-warming operation.

FIG. 6 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation.

FIG. 7 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation.

FIG. 8 is a flowchart of the air-cooling start control.

FIG. 9 is a diagram showing the flow of refrigerant within the air-conditioning apparatus during the air-cooling start control.

FIG. 10 is a schematic structural diagram of an air-conditioning apparatus according to Modification 1.

FIG. 11 is an external perspective view of a heat source unit (the fan grill having been removed).

FIG. 12 is a side view of the heat source unit in which the right plate of the heat source unit has been removed.

FIG. 13 is a diagram showing the characteristics of the heat transfer coefficient when carbon dioxide of an intermediate pressure lower than the critical pressure is flowing into the heat transfer channel, and of the heat transfer coefficient when carbon dioxide of a high pressure exceeding the critical pressure is flowing into the heat transfer channel.

FIG. 14 is a schematic structural diagram of an air-conditioning apparatus according to Modification 3.

FIG. 15 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according to Modification 3.

FIG. 16 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according to Modification 3.

FIG. 17 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according to Modification 3.

FIG. 18 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according to Modification 3.

FIG. 19 is a schematic structural diagram of an air-conditioning apparatus according to Modification 4.

FIG. 20 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according to Modification 4.

FIG. 21 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation in the air-conditioning apparatus according to Modification 4.

FIG. 22 is a schematic structural diagram of an air-conditioning apparatus according to Modification 5.

FIG. 23 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according to Modification 5.

FIG. 24 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation in the air-conditioning apparatus according to Modification 5.

FIG. 25 is a schematic structural diagram of an air-conditioning apparatus according to Modification 6.

FIG. 26 is a schematic structural diagram of an air-conditioning apparatus according to Modification 7.

FIG. 27 is a schematic structural diagram of an air-conditioning apparatus according to Modification 8.

FIG. 28 is a schematic structural diagram of an air-conditioning apparatus according to Modification 9.

FIG. 29 is a schematic structural diagram of an air-conditioning apparatus according to Modification 10.

FIG. 30 is a schematic structural diagram of an air-conditioning apparatus according to Modification 11.

FIG. 31 is a schematic structural diagram of an air-conditioning apparatus according to Modification 11.

FIG. 32 is a schematic structural diagram of an air-conditioning apparatus according to Modification 12.

FIG. 33 is a schematic structural diagram of an air-conditioning apparatus according to Modification 13.

EXPLANATION OF THE REFERENCE NUMERALS

-   -   1 Air-conditioning apparatus (refrigeration apparatus)     -   2, 102, 202, 302 Compression mechanism     -   3 Switching mechanism     -   4 Heat source-side heat exchanger     -   6 Usage-side heat exchanger     -   7, 307 Intermediate heat exchanger     -   8, 308 Intermediate refrigerant tube     -   9, 309 Intermediate heat exchanger bypass tube     -   92, 392 Second intake return tube     -   94, 394 Intermediate heat exchanger return tube     -   94 b, 394 b Intermediate heat exchanger return valve (flow rate         control valve)     -   97 Expansion device     -   17 Rectifier circuit (bridge circuit)     -   18 Receiver (gas-liquid separator)     -   18 c Second second-stage injection tube

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiments of the refrigeration apparatus according to the present invention are described hereinbelow with reference to the drawings.

(1) Configuration of Air-Conditioning Apparatus

FIG. 1 is a schematic structural diagram of an air-conditioning apparatus 1 as an embodiment of the refrigeration apparatus according to the present invention. The air-conditioning apparatus 1 has a refrigerant circuit 10 configured to be capable of switching between an air-cooling operation and an air-warming operation, and the apparatus performs a two-stage compression refrigeration cycle by using a refrigerant (carbon dioxide in this case) for operating in a supercritical range.

The refrigerant circuit 10 of the air-conditioning apparatus 1 primarily has a compression mechanism 2, a switching mechanism 3, a heat source-side heat exchanger 4, a bridge circuit 17, a receiver 18, a first expansion mechanism 5 a, a second expansion mechanism 5 b, a usage-side heat exchanger 6, and an intermediate heat exchanger 7.

In the present embodiment, the compression mechanism 2 is configured from a compressor 21 which uses two compression elements to subject a refrigerant to two-stage compression. The compressor 21 has a hermetic structure in which a compressor drive motor 21 b, a drive shaft 21 c, and compression elements 2 c, 2 d are housed within a casing 21 a. The compressor drive motor 21 b is linked to the drive shaft 21 c. The drive shaft 21 c is linked to the two compression elements 2 c, 2 d. Specifically, the compressor 21 has a so-called single-shaft two-stage compression structure in which the two compression elements 2 c, 2 d are linked to a single drive shaft 21 c and the two compression elements 2 c, 2 d are both rotatably driven by the compressor drive motor 21 b. In the present embodiment, the compression elements 2 c, 2 d are rotary elements, scroll elements, or another type of positive displacement compression element. The compressor 21 is configured so as to admit refrigerant through an intake tube 2 a, to discharge this refrigerant to an intermediate refrigerant tube 8 after the refrigerant has been compressed by the compression element 2 c, to draw the refrigerant discharged to the intermediate refrigerant tube 8 into the compression element 2 d, and to discharge the refrigerant to a discharge tube 2 b after the refrigerant has been further compressed. The intermediate refrigerant tube 8 is a refrigerant tube for drawing refrigerant into the compression element 2 d connected to the second-stage side of the compression element 2 c after the refrigerant has been discharged at an intermediate pressure in the refrigeration cycle from the compression element 2 c connected to the first-stage side of the compression element 2 d. The discharge tube 2 b is a refrigerant tube for feeding refrigerant discharged from the compression mechanism 2 to the switching mechanism 3, and the discharge tube 2 b is provided with an oil separation mechanism 41 and a non-return mechanism 42. The oil separation mechanism 41 is a mechanism for separating refrigerator oil accompanying the refrigerant from the refrigerant discharged from the compression mechanism 2 and returning the oil to the intake side of the compression mechanism 2, and the oil separation mechanism 41 has primarily an oil separator 41 a for separating refrigerator oil accompanying the refrigerant from the refrigerant discharged from the compression mechanism 2, and an oil return tube 41 b connected to the oil separator 41 a for returning the refrigerator oil separated from the refrigerant to the intake tube 2 a of the compression mechanism 2. The oil return tube 41 b is provided with a pressure-reducing mechanism 41 c for depressurizing the refrigerator oil flowing through the oil return tube 41 b. A capillary tube is used for the pressure-reducing mechanism 41 c in the present embodiment. The non-return mechanism 42 is a mechanism for allowing the flow of refrigerant from the discharge side of the compression mechanism 2 to the heat source-side heat exchanger 4 as a radiator and for blocking the flow of refrigerant from the heat source-side heat exchanger 4 as a radiator to the discharge side of the compression mechanism 2, and a non-return valve is used in the present embodiment.

Thus, in the present embodiment, the compression mechanism 2 has two compression elements 2 c, 2 d and is configured so that among these compression elements 2 c, 2 d, refrigerant discharged from the first-stage compression element is compressed in sequence by the second-stage compression element.

The switching mechanism 3 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10. In order to allow the heat source-side heat exchanger 4 to function as a refrigerant radiator compressed by the compression mechanism 2 and to allow the usage-side heat exchanger 6 to function as an evaporator of refrigerant cooled in the heat source-side heat exchanger 4 during the air-cooling operation, the switching mechanism 3 is capable of connecting the discharge side of the compression mechanism 2 and one end of the heat source-side heat exchanger 4 and also connecting the intake side of the compressor 21 and the usage-side heat exchanger 6 (refer to the solid lines of the switching mechanism 3 in FIG. 1, this state of the switching mechanism 3 is hereinbelow referred to as the “cooling operation state”). In order to allow the usage-side heat exchanger 6 to function as a refrigerant radiator compressed by the compression mechanism 2 and to allow the heat source-side heat exchanger 4 to function as an evaporator of refrigerant cooled in the usage-side heat exchanger 6 during the air-warming operation, the switching mechanism 3 is capable of connecting the discharge side of the compression mechanism 2 and the usage-side heat exchanger 6 and also of connecting the intake side of the compression mechanism 2 and one end of the heat source-side heat exchanger 4 (refer to the dashed lines of the switching mechanism 3 in FIG. 1, this state of the switching mechanism 3 is hereinbelow referred to as the “heating operation state”). In the present embodiment, the switching mechanism 3 is a four-way switching valve connected to the intake side of the compression mechanism 2, the discharge side of the compression mechanism 2, the heat source-side heat exchanger 4, and the usage-side heat exchanger 6. The switching mechanism 3 is not limited to a four-way switching valve, and may be configured so as to have a function for switching the direction of the flow of the refrigerant in the same manner as described above by using, e.g., a combination of a plurality of electromagnetic valves.

Thus, focusing solely on the compression mechanism 2, the heat source-side heat exchanger 4, and the usage-side heat exchanger 6 constituting the refrigerant circuit 10; the switching mechanism 3 is configured so as to be capable of switching between the cooling operation state in which refrigerant is circulated in sequence through the compression mechanism 2, the heat source-side heat exchanger 4 functioning as a radiator of the refrigerant, and the usage-side heat exchanger 6 functioning as an evaporator of the refrigerant; and the heating operation state in which refrigerant is circulated in sequence through the compression mechanism 2, the usage-side heat exchanger 6 functioning as a radiator of the refrigerant, and the heat source-side heat exchanger 4 functioning as an evaporator of the refrigerant.

The heat source-side heat exchanger 4 is a heat exchanger that functions as a radiator or an evaporator of refrigerant. One end of the heat source-side heat exchanger 4 is connected to the switching mechanism 3, and the other end is connected to the first expansion mechanism 5 a via the bridge circuit 17. Though not shown in the drawings, the heat source-side heat exchanger 4 is supplied with water or air as a cooling source for conducting heat exchange with the refrigerant flowing through the heat source-side heat exchanger 4.

The bridge circuit 17 is disposed between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6, and is connected to a receiver inlet tube 18 a connected to the inlet of the receiver 18 and to a receiver outlet tube 18 b connected to the outlet of the receiver 18. The bridge circuit 17 has four non-return valves 17 a, 17 b, 17 c, 17 d in the present embodiment. The inlet non-return valve 17 a is a non-return valve that allows only the flow of refrigerant from the heat source-side heat exchanger 4 to the receiver inlet tube 18 a. The inlet non-return valve 17 b is a non-return valve that allows only the flow of refrigerant from the usage-side heat exchanger 6 to the receiver inlet tube 18 a. In other words, the inlet non-return valves 17 a, 17 b have a function for allowing refrigerant to flow from one among the heat source-side heat exchanger 4 and the usage-side heat exchanger 6 to the receiver inlet tube 18 a. The outlet non-return valve 17 c is a non-return valve that allows only the flow of refrigerant from the receiver outlet tube 18 b to the usage-side heat exchanger 6. The outlet non-return valve 17 d is a non-return valve that allows only the flow of refrigerant from the receiver outlet tube 18 b to the heat source-side heat exchanger 4. In other words, the outlet non-return valves 17 c, 17 d have a function for allowing refrigerant to flow from the receiver outlet tube 18 b to the heat source-side heat exchanger 4 or the usage-side heat exchanger 6.

The first expansion mechanism 5 a is a mechanism for depressurizing the refrigerant, is provided to the receiver inlet tube 18 a, and is an electrically driven expansion valve in the present embodiment. In the present embodiment, the first expansion mechanism 5 a depressurizes the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 to a nearly saturated pressure before feeding the refrigerant to the usage-side heat exchanger 6 via the receiver 18 during the air-cooling operation, and depressurizes the high-pressure refrigerant cooled in the usage-side heat exchanger 6 to a nearly saturated pressure before feeding the refrigerant to the heat source-side heat exchanger 4 via the receiver 18 during the air-warming operation.

The receiver 18 is a container provided in order to temporarily accumulate refrigerant that has been depressurized by the first expansion mechanism 5 a, so that it is possible to collect excess refrigerant which may be produced depending on operation states in which the quantity of refrigerant circulated in the refrigerant circuit 10 differs between the air-cooling operation and the air-warming operation, for example. The inlet of the receiver 18 is connected to the receiver inlet tube 18 a and the outlet is connected to the receiver outlet tube 18 b. Also connected to the receiver 18 is a first intake return tube 18 f capable of withdrawing refrigerant from inside the receiver 18 and returning the refrigerant to the intake tube 2 a of the compression mechanism 2 (i.e., to the intake side of the compression element 2 c on the first-stage side of the compression mechanism 2). This first intake return tube 18 f is provided with a first intake return on/off valve 18 g. The first intake return on/off valve 18 g is an electromagnetic valve in the present embodiment.

The second expansion mechanism 5 b is a mechanism provided to the receiver outlet tube 18 b and used for depressurizing the refrigerant, and is an electrically driven expansion valve in the present embodiment. In the present embodiment, in the second expansion mechanism 5 b, the refrigerant depressurized by the first expansion mechanism 5 a is further depressurized during the air-cooling operation to a low pressure in the refrigeration cycle prior to being fed to the usage-side heat exchanger 6 via the receiver 18, and the refrigerant depressurized by the first expansion mechanism 5 a is further depressurized during the air-warming operation to a low pressure in the refrigeration cycle prior to being sent to the heat source-side heat exchanger 4 via the receiver 18.

The usage-side heat exchanger 6 is a heat exchanger that functions as an evaporator or refrigerant radiator. One end of the usage-side heat exchanger 6 is connected to the first expansion mechanism 5 a via the bridge circuit, and the other end is connected to the switching mechanism 3. Though not shown in the drawings, the usage-side heat exchanger 6 is supplied with water or air as a heating source for conducting heat exchange with the refrigerant flowing through the usage-side heat exchanger 6.

Thus, in the present embodiment, when the switching mechanism 3 is brought to the cooling operation state by the bridge circuit 17, the receiver 18, the receiver inlet tube 18 a, and the receiver outlet tube 18 b, the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 can be fed to the usage-side heat exchanger 6 through the inlet non-return valve 17 a of the bridge circuit 17, the first expansion mechanism 5 a of the receiver inlet tube 18 a, the receiver 18, the second expansion mechanism 5 b of the receiver outlet tube 18 b, and the outlet non-return valve 17 c of the bridge circuit 17. When the switching mechanism 3 is brought to the heating operation state, the high-pressure refrigerant cooled in the usage-side heat exchanger 6 can be fed to the heat source-side heat exchanger 4 through the inlet non-return valve 17 b of the bridge circuit 17, the first expansion mechanism 5 a of the receiver inlet tube 18 a, the receiver 18, the second expansion mechanism 5 b of the receiver outlet tube 18 b, and the outlet non-return valve 17 d of the bridge circuit 17.

The intermediate heat exchanger 7 is provided to the intermediate refrigerant tube 8, and is either a cooler of the refrigerant discharged from the first-stage compression element 2 c and drawn into the compression element 2 d, or a heat exchanger capable of functioning as an evaporator of the refrigerant whose heat has been radiated in the usage-side heat exchanger 6. Though not shown in the drawings, the intermediate heat exchanger 7 is supplied with water or air as a cooling source for conducting heat exchange with the refrigerant flowing through the intermediate heat exchanger 7. Thus, it is acceptable to say that the intermediate heat exchanger 7 is a cooler that uses an external heating source, meaning that the intermediate heat exchanger does not use the refrigerant that circulates through the refrigerant circuit 10.

An intermediate heat exchanger bypass tube 9 is connected to the intermediate refrigerant tube 8 so as to bypass the intermediate heat exchanger 7. This intermediate heat exchanger bypass tube 9 is a refrigerant tube for limiting the flow rate of refrigerant flowing through the intermediate heat exchanger 7. The intermediate heat exchanger bypass tube 9 is provided with an intermediate heat exchanger bypass on/off valve 11. The intermediate heat exchanger bypass on/off valve 11 is an electromagnetic valve in the present embodiment. Excluding cases in which temporary operations such as the hereinafter-described air-cooling start control are performed, in the present embodiment the intermediate heat exchanger bypass on/off valve 11 is essentially controlled so as to close when the switching mechanism 3 is set for the cooling operation state, and to open when the switching mechanism 3 is set for the heating operation state. In other words, the intermediate heat exchanger bypass on/off valve 11 is closed when the air-cooling operation is performed and opened when the air-warming operation is performed.

In the intermediate refrigerant tube 8, an intermediate heat exchanger on/off valve 12 is provided to the portion extending from the connection with the end of the intermediate heat exchanger bypass tube 9 near the first-stage compression element 2 c to the end of the intermediate heat exchanger 7 near the first-stage compression element 2 c. This intermediate heat exchanger on/off valve 12 is a mechanism for limiting the flow rate of refrigerant flowing through the intermediate heat exchanger 7. The intermediate heat exchanger on/off valve 12 is an electromagnetic valve in the present embodiment. Excluding cases in which temporary operations such as the hereinafter-described air-cooling start control are performed, in the present embodiment the intermediate heat exchanger on/off valve 12 is essentially controlled so as to open when the switching mechanism 3 is set for the cooling operation state, and to close when the switching mechanism 3 is set for the heating operation state. In other words, the intermediate heat exchanger on/off valve 12 is controlled so as to open when the air-cooling operation is performed and close when the air-warming operation is performed.

The intermediate refrigerant tube 8 is also provided with a non-return mechanism 15 for allowing refrigerant to flow from the discharge side of the first-stage compression element 2 c to the intake side of the second-stage compression element 2 d and for blocking the refrigerant from flowing from the intake side of the second-stage compression element 2 d to the discharge side of the first-stage compression element 2 c. The non-return mechanism 15 is a non-return valve in the present embodiment. In the present embodiment, the non-return mechanism 15 is provided to the intermediate refrigerant tube 8 in the portion extending from the end of the intermediate heat exchanger 7 near the second-stage compression element 2 d to the connection with the end of the intermediate heat exchanger bypass tube 9 near the second-stage compression element 2 d.

Furthermore, a second intake return tube 92 is connected to one end of the intermediate heat exchanger 7 (here, the end near the first-stage compression element 2 c), and an intermediate heat exchanger return tube 94 is connected to the other end of the intermediate heat exchanger 7 (herein, the end near the second-stage compression element 2 d). This second intake return tube 92 is a refrigerant tube for connecting one end of the intermediate heat exchanger 7 and the intake side of the compressor 2 (here, the intake tube 2 a) during a state in which the refrigerant discharged from the first-stage compression element 2 c is being drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9. The intermediate heat exchanger return tube 94 is a refrigerant tube for connecting the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4 (here, the portion between the second expansion mechanism 5 b which depressurizes the refrigerant to a low pressure in the refrigeration cycle and the heat source-side heat exchanger 4 as an evaporator) with the other end of the intermediate heat exchanger 7, when the refrigerant discharged from the first-stage compression element 2 c is being drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9 and the switching mechanism 3 has been set to the heating operation state. In the present embodiment, the second intake return tube 92 is connected at one end to the portion of the intermediate refrigerant tube 8 extending from the connection with the end of the intermediate heat exchanger bypass tube 9 near the first-stage compression element 2 c to the end of the intermediate heat exchanger 7 near the first-stage compression element 2 c, while the other end is connected to the intake side of the compressor 2 (here, the intake tube 2 a). One end of the intermediate heat exchanger return tube 94 is connected to the portion extending from the second expansion mechanism 5 b to the heat source-side heat exchanger 4, while the other end is connected to the portion of the intermediate refrigerant tube 8 extending from the end of the intermediate heat exchanger 7 near the first-stage compression element 2 c to the non-return mechanism 15. The second intake return tube 92 is also provided with a second intake return on/off valve 92 a, and the intermediate heat exchanger return tube 94 is provided with an intermediate heat exchanger return on/off valve 94 a. The second intake return on/off valve 92 a and the intermediate heat exchanger return on/off valve 94 a are electromagnetic valves in the present embodiment. Excluding cases in which temporary operations such as the hereinafter-described air-cooling start control are performed, in the present embodiment the second intake return on/off valve 92 a is essentially controlled so as to close when the switching mechanism 3 is set for the cooling operation state, and to open when the switching mechanism 3 is set for the heating operation state. The intermediate heat exchanger return on/off valve 94 a is controlled so as to close when the switching mechanism 3 is set for the cooling operation state and to open when the switching mechanism 3 is set for the heating operation state, including cases in which temporary operations such as the hereinafter-described air-cooling start control are performed.

Thus, in the present embodiment, owing primarily to the intermediate heat exchanger bypass tube 9, the second intake return tube 92, and the intermediate heat exchanger return tube 94, the intermediate-pressure refrigerant flowing through the intermediate refrigerant tube 8 can be cooled by the intermediate heat exchanger 7 during the air-cooling operation; and during the air-warming operation, the intermediate-pressure refrigerant flowing through the intermediate refrigerant tube 8 can be made to bypass the intermediate heat exchanger 7 by the intermediate heat exchanger bypass tube 9, and some of the refrigerant cooled in the usage-side heat exchanger 6 can be drawn into and evaporated in the intermediate heat exchanger 7 and returned to the intake side of the compression mechanism 2 by the second intake return tube 92 and the intermediate heat exchanger return tube 94.

Furthermore, though not shown in the drawings, the air-conditioning apparatus 1 has a controller for controlling the actions of the components constituting the air-conditioning apparatus 1, including the compression mechanism 2, the switching mechanism 3, the expansion mechanisms 5 a, 5 b, the intermediate heat exchanger bypass on/off valve 11, the intermediate heat exchanger on/off valve 12, the first intake return on/off valve 18 g, the second intake return on/off valve 92 a, the intermediate heat exchanger return on/off valve 94 a, and the like.

(2) Action of the Air-Conditioning Apparatus

Next, the action of the air-conditioning apparatus 1 of the present embodiment will be described using FIGS. 1 through 9. FIG. 2 is a diagram showing the flow of refrigerant within the air-conditioning apparatus 1 during the air-cooling operation, FIG. 3 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation, FIG. 4 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation, FIG. 5 is a diagram showing the flow of refrigerant within the air-conditioning apparatus 1 during the air-warming operation, FIG. 6 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation, FIG. 7 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation, FIG. 8 is a flowchart of air-cooling start control, and FIG. 9 is a diagram showing the flow of refrigerant within the air-conditioning apparatus 1 during air-cooling start control. Operation control and air-cooling start control during the following air-cooling operation and air-warming operation are performed by the aforementioned controller (not shown). In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, and E in FIGS. 3 and 4, and the pressure at points D, D′, and F in FIGS. 6 and 7), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A and F in FIGS. 3 and 4, and the pressure at points A, E, and V in FIGS. 6 and 7), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1 and C1 in FIGS. 3 and 4; and the pressure at points B1, C1, and C1′ in FIGS. 6 and 7).

<Air-Cooling Operation>

During the air-cooling operation, the switching mechanism 3 is brought to the cooling operation state shown by the solid lines in FIGS. 1 and 2. The opening degrees of the first expansion mechanism 5 a and the second expansion mechanism 5 b are adjusted. Since the switching mechanism 3 is set for the cooling operation state, the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 is opened and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is closed, whereby the intermediate heat exchanger 7 is set to function as a cooler. Additionally, the second intake return on/off valve 92 a of the second intake return tube 92 is closed, thereby creating a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected (except when air-cooling start control is in effect, described hereinafter), and the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 is closed, thereby creating a state in which the intermediate heat exchanger 7 is not connected with the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4.

When the refrigerant circuit 10 is in this state, low-pressure refrigerant (refer to point A in FIGS. 1 through 4) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 1 through 4). The intermediate-pressure refrigerant discharged from the first-stage compression element 2 c is cooled by heat exchange with water or air as a cooling source in the intermediate heat exchanger 7 (refer to point C1 in FIGS. 1 to 4). The refrigerant cooled in the intermediate heat exchanger 7 is then drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is then discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 1 through 4). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 3). The high-pressure refrigerant discharged from the compression mechanism 2 flows into the oil separator 41 a constituting the oil separation mechanism 41, and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in the oil separator 41 a flows into the oil return tube 41 b constituting the oil separation mechanism 41 wherein it is depressurized by the pressure-reducing mechanism 41 c provided to the oil return tube 41 b, and the oil is then returned to the intake tube 2 a of the compression mechanism 2 and drawn back into the compression mechanism 2. Next, having been separated from the refrigeration oil in the oil separation mechanism 41, the high-pressure refrigerant is passed through the non-return mechanism 42 and the switching mechanism 3, and is fed to the heat source-side heat exchanger 4 functioning as a refrigerant radiator. The high-pressure refrigerant fed to the heat source-side heat exchanger 4 is cooled in the heat source-side heat exchanger 4 by heat exchange with water or air as a cooling source (refer to point E in FIGS. 2 through 4). The high-pressure refrigerant cooled in the heat source-side heat exchanger 4 then flows into the receiver inlet tube 18 a through the inlet non-return valve 17 a of the bridge circuit 17, and the refrigerant is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained inside the receiver 18 (refer to point I in FIGS. 1 and 2). The refrigerant retained in the receiver 18 is fed to the receiver outlet tube 18 b and is depressurized by the second expansion mechanism 5 b to become a low-pressure gas-liquid two-phase refrigerant, and is then fed through the outlet non-return valve 17 c of the bridge circuit 17 to the usage-side heat exchanger 6 functioning as a refrigerant evaporator (refer to point F in FIGS. 1 to 4). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchanger 6 is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A in FIGS. 1 to 4). The low-pressure refrigerant heated in the usage-side heat exchanger 6 is then drawn back into the compression mechanism 2 via the switching mechanism 3. In this manner the air-cooling operation is performed.

Thus, in the air-conditioning apparatus 1 of the present embodiment, the intermediate heat exchanger 7 is provided to the intermediate refrigerant tube 8 for drawing refrigerant discharged from the compression element 2 c into the compression element 2 d, and in the air-cooling operation the intermediate heat exchanger on/off valve 12 is opened and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is closed, thereby putting the intermediate heat exchanger 7 into a state of functioning as a cooler. Therefore, the refrigerant drawn into the compression element 2 d on the second-stage side of the compression element 2 c decreases in temperature (refer to points B1 and C1 in FIG. 4) and the refrigerant discharged from the compression element 2 d also decreases in temperature (refer to points D and D′ in FIG. 4), in comparison with cases in which no intermediate heat exchanger 7 is provided (in this case, the refrigeration cycle is performed in the sequence in FIGS. 3 and 4: point A→point B1→point D′→point E→point F). Therefore, in the heat source-side heat exchanger 4 functioning as a radiator of high-pressure refrigerant in this air-conditioning apparatus 1, operating efficiency can be improved over cases in which no intermediate heat exchanger 7 is provided, because the temperature difference between the refrigerant and water or air as the cooling source can be reduced, and heat radiation loss can be reduced by an amount equivalent to the area enclosed by connecting points B1, D′, D, and C1 in FIG. 4.

<Air-Warming Operation>

During the air-warming operation, the switching mechanism 3 is brought to the heating operation state shown by the dashed lines in FIGS. 1 and 5. The opening degrees of the first expansion mechanism 5 a and the second expansion mechanism 5 b are also adjusted. Since the switching mechanism 3 is set to a heating operation state, the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 is closed and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is opened, thereby putting the intermediate heat exchanger 7 into a state of not functioning as a cooler. Furthermore, since the switching mechanism 3 is set for the heating operation, the second intake return on/off valve 92 a of the second intake return tube 92 is opened, thereby creating a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected, and the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 is also opened, thereby creating a state in which the intermediate heat exchanger 7 is connected with the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4.

When the refrigerant circuit 10 is in this state, low-pressure refrigerant (refer to point A in FIG. 1 and FIGS. 5-7) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIG. 1 and FIGS. 5 through 7). The intermediate-pressure refrigerant discharged from the first-stage compression element 2 c passes through the intermediate heat exchanger bypass tube 9 (refer to point C1 in FIG. 1 and FIGS. 5 through 7) without passing through the intermediate heat exchanger 7 (i.e., without being cooled), unlike in the air-cooling operation. The refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIG. 1 and FIGS. 5 through 7). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 6), similar to the air-cooling operation. The high-pressure refrigerant discharged from the compression mechanism 2 flows into the oil separator 41 a constituting the oil separation mechanism 41, and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in the oil separator 41 a flows into the oil return tube 41 b constituting the oil separation mechanism 41 wherein it is depressurized by the pressure-reducing mechanism 41 c provided to the oil return tube 41 b, and the oil is then returned to the intake tube 2 a of the compression mechanism 2 and drawn back into the compression mechanism 2. Next, having been separated from the refrigeration oil in the oil separation mechanism 41, the high-pressure refrigerant is passed through the non-return mechanism 42 and the switching mechanism 3, is fed to the usage-side heat exchanger 6 functioning as a refrigerant radiator, and is cooled by heat exchange with water or air as a cooling source (refer to point F in FIG. 1 and FIGS. 5 to 7). The high-pressure refrigerant cooled in the usage-side heat exchanger 6 then flows into the receiver inlet tube 18 a through the inlet non-return valve 17 b of the bridge circuit 17, and the refrigerant is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained inside the receiver 18 (refer to point I in FIGS. 1 and 5). The refrigerant retained inside the receiver 18 is fed to the receiver outlet tube 18 b and is depressurized by the second expansion mechanism 5 b into a low-pressure gas-liquid two-phase refrigerant, which is then fed through the outlet non-return valve 17 d of the bridge circuit 17 to the heat source-side heat exchanger 4 functioning as an evaporator of refrigerant, and is also fed through the intermediate heat exchanger return tube 94 to the intermediate heat exchanger 7 functioning as an evaporator of refrigerant (refer to point E in FIG. 1 and FIGS. 5 to 7). The low-pressure gas-liquid two-phase refrigerant fed to the heat source-side heat exchanger 4 is heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point A in FIGS. 1, 5 through 7). The low-pressure gas-liquid two-phase refrigerant fed to the intermediate heat exchanger 7 is also heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point V in FIGS. 1, 5 through 7). The low-pressure refrigerant heated and evaporated in the heat source-side heat exchanger 4 is then drawn back into the compression mechanism 2 via the switching mechanism 3. The low-pressure refrigerant heated and evaporated in the intermediate heat exchanger 7 is then drawn back into the compression mechanism 2 via the second intake return tube 92. In this manner the air-warming operation is performed.

Thus, in the air-conditioning apparatus 1 of the present embodiment, during the air-warming operation in which the switching mechanism 3 is set to the heating operation state, the intermediate heat exchanger on/off valve 12 is closed and the intermediate heat exchanger bypass on/off valve 11 is opened, thereby putting the intermediate heat exchanger 7 into a state of not functioning as a cooler. Therefore, the temperature decrease is minimized in the refrigerant discharged from the compression mechanism 2 (refer to points D and D′ in FIG. 7), in comparison with cases in which only the intermediate heat exchanger 7 is provided and/or cases in which the intermediate heat exchanger 7 is made to function as a cooler similar to the air-cooling operation described above (in these cases, the refrigeration cycle is performed in the sequence in FIGS. 6 and 7: point A→point B1→point C1′→point D′→point F→point E). Therefore, in the air-conditioning apparatus 1, heat radiation to the exterior can be minimized, temperature decreases can be minimized in the refrigerant supplied to the usage-side heat exchanger 6 functioning as a refrigerant radiator, loss of heating performance can be minimized in proportion to the difference between the enthalpy difference of points D and F and the enthalpy difference of points D′ and F in FIG. 7, and loss of operating efficiency can be prevented, in comparison with cases in which only the intermediate heat exchanger 7 is provided and/or cases in which the intermediate heat exchanger 7 is made to function as a cooler similar to the air-cooling operation described above.

Moreover, in the air-conditioning apparatus 1 of the present embodiment, during the air-warming operation in which the switching mechanism 3 is set for the heating operation state, the intermediate heat exchanger 7 is not merely set to a state of not functioning as a cooler due to not being used. Instead, the intermediate heat exchanger 7, along with the heat source-side heat exchanger 4, is made to function as an evaporator of the refrigerant whose heat has been radiated in the usage-side heat exchanger 6, and is used during the air-warming operation as well to increase refrigerant-evaporating capacity during the air-warming operation and to increase the quantity of refrigerant circulating within the refrigerant circuit 10 while minimizing the heat radiated from the intermediate heat exchanger 7 to the exterior, for example, thereby minimizing the decrease in heating capacity in the usage-side heat exchanger 6. Thereby, in the air-conditioning apparatus 1 of the present embodiment, heat radiation loss decreases in the heat source-side heat exchanger 4 functioning as a refrigerant radiator during the air-cooling operation, and operating efficiency during the air-cooling operation can be improved. During the air-warming operation, it is possible to use the intermediate heat exchanger 7 more effectively, minimize the reduction in the heating capacity of the heat source-side heat exchanger 6, and prevent operating efficiency during the air-warming operation from decreasing.

<Air-Cooling Start Control>

With the intermediate heat exchanger 7 described above, there is a risk of liquid refrigerant accumulating when the air-conditioning apparatus 1 has stopped, or in other instances. When the above-described air-cooling operation is started during a state in which liquid refrigerant has accumulated in the intermediate heat exchanger 7, the liquid refrigerant accumulated in the intermediate heat exchanger 7 is drawn into the second-stage compression element 2 d; therefore, the liquid begins to be compressed in the second-stage compression element 2 d, and the reliability of the compression mechanism 2 is compromised.

In view whereof, in the present embodiment, during the start of the above-described air-cooling operation, a state is created in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9, and air-cooling start control is performed in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected by the second intake return tube 92.

The air-cooling start control of the present embodiment is described in detail hereinbelow using FIGS. 8 and 9.

First, in step S1, when a command to start the air-cooling operation is issued, the process advances to operating the various valves in step S2.

Next, in step S2, the on/off state of the on/off valves 11, 12, 92 a is switched to a refrigerant return state in which the refrigerant discharged from the first-stage compression element 2 c through the intermediate heat exchanger bypass tube 9 is drawn into the second-stage compression element 2 d, and the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected through the second intake return tube 92. Specifically, the intermediate heat exchanger bypass on/off valve 11 is opened and the intermediate heat exchanger on/off valve 12 is closed. A flow is thus created by the intermediate heat exchanger bypass tube 9 in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d without passing through the intermediate heat exchanger 7. In other words, the intermediate heat exchanger 7 is put into a state of not functioning as a cooler, and a state is created in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9 (see FIG. 9). In this type of state, the second intake return on/off valve 92 a is opened. The intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are then connected by the second intake return tube 92, the pressure of the refrigerant in the intermediate heat exchanger 7 (more specifically, in the portion between the intermediate heat exchanger on/off valve 12 and the non-return mechanism 15 which includes the intermediate heat exchanger 7) decreases nearly to the low pressure of the refrigeration cycle, and a state is created in which the refrigerant inside the intermediate heat exchanger 7 can be withdrawn into the intake side of the compression mechanism 2 (see FIG. 9).

Next, in step S3, the on/off state of the on/off valves 11, 12, 92 a in step S2 (i.e., the refrigerant return state) is maintained for a predetermined time duration. Thereby, even if liquid refrigerant has accumulated in the intermediate heat exchanger 7 while the air-conditioning apparatus 1 has been stopped, for example, the liquid refrigerant accumulated inside the intermediate heat exchanger 7 is depressurized and evaporated, then removed out of the intermediate heat exchanger 7 (more specifically, to the intake side of the compression mechanism 2) without being drawn into the second-stage compression element 2 d, and is drawn into the compression mechanism 2 (the first-stage compression element 2 c, in this case). The predetermined time duration is herein set to a time duration whereby the liquid refrigerant accumulating in the intermediate heat exchanger 7 can be drawn out of the intermediate heat exchanger 7.

Next, in step S4, the on/off state of the on/off valves 11, 12, 92 a is switched to a refrigerant non-return state in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger 7, and the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected through the second intake return tube 92. In other words, a transition is made to the on/off state of the valves 11, 12, 92 a during the above-described air-cooling operation, and the air-cooling start control is ended. Specifically, the second intake return on/off valve 92 a is closed. A state is thus created in which the refrigerant inside the intermediate heat exchanger 7 does not flow out to the intake side of the compression mechanism 2. In this type of state, the intermediate heat exchanger on/off valve 12 is then opened, and the intermediate heat exchanger bypass on/off valve 11 is closed. A state is thus created in which the intermediate heat exchanger 7 functions as a cooler.

Thereby, in the air-conditioning apparatus 1, during the start of the air-cooling operation, there is no liquid compression in the second-stage compression element 2 d, which would occur as a result of liquid refrigerant accumulating in the intermediate heat exchanger 7, and the reliability of the compression mechanism 2 can be improved.

(3) Modification 1

In the embodiment described above, switching between the air-cooling operation and air-cooling start control, i.e., switching between the refrigerant non-return state and the refrigerant return state was performed by changing the on/off state of the on/off valves 11, 12, 92 a, but another option is a refrigerant circuit 110 as shown in FIG. 10, wherein an intermediate heat exchanger switching valve 93 capable of switching between the refrigerant non-return state and the refrigerant return state is provided instead of the on/off valves 11, 12, 92 a.

The intermediate heat exchanger switching valve 93 herein is a valve capable of switching between the refrigerant non-return state and the refrigerant return state, and in the present modification is a four-way switching valve connected to the discharge side of the first-stage compression element 2 c of the intermediate refrigerant tube 8, the inlet side of the intermediate heat exchanger 7 of the intermediate refrigerant tube 8, the end of the intermediate heat exchanger bypass tube 9 on the side near the first-stage compression element 2 c, and the end of the second intake return tube 92 on the side near the intermediate heat exchanger 7. The intermediate heat exchanger bypass tube 9 is also provided with a non-return mechanism 9 a for allowing refrigerant to flow from the discharge side of the first-stage compression element 2 c to the intake side of the second-stage compression element 2 d and for blocking the refrigerant from flowing from the intake side of the second-stage compression element 2 d to the discharge side of the first-stage compression element 2 c and the intake side of the compression mechanism 2. The non-return mechanism 9 a is a non-return valve in the present modification.

In the present modification, although a detailed description is not given, the same air-cooling operation as in the embodiment described above can be performed by switching the intermediate heat exchanger switching valve 93 to the refrigerant non-return state (refer to the solid lines of the intermediate heat exchanger switching valve 93 in FIG. 10) in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger 7 and the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected through the second intake return tube 92, and the same air-warming operation and/or air-cooling start control as in the embodiment described above can be performed by switching the intermediate heat exchanger switching valve 93 to the refrigerant return state (refer to the dashed lines of the intermediate heat exchanger switching valve 93 in FIG. 10) in which the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9 and the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected through the second intake return tube 92.

The same operational effects as those of the embodiment described above can also be achieved with the configuration of the present modification. Moreover, in the present modification, since the refrigerant non-return state and the refrigerant return state can be switched by the intermediate heat exchanger switching valve 93, the number of valves can be reduced in comparison with the case of using the configuration in which the refrigerant non-return state and the refrigerant return state are switched by a plurality of valves 11, 12, 92 a such as those of the embodiment described above. Since pressure loss is reduced in comparison with cases of using electromagnetic valves, the decrease in intermediate pressure in the refrigeration cycle can be minimized, and the decrease operating efficiency can also be minimized.

(4) Modification 2

In the above-described embodiment and the modification thereof, consideration is given to using a configuration in which the intermediate heat exchanger 7 and the heat source-side heat exchanger 4 are heat exchangers that use air as a heat source (that is, as a cooling source or a heating source), and air as a heat source is supplied by a common heat source-side fan 40 (described hereinafter) to both heat exchangers 4, 7.

For example, in cases in which the air-conditioning apparatus 1 has a configuration in which a heat source unit 1 a provided primarily with the heat source-side fan 40, the heat source-side heat exchanger 4, and the intermediate heat exchanger 7 is connected with a usage unit (not shown) provided primarily with the usage-side heat exchanger 6, the heat source unit 1 a such as is shown in FIGS. 11 and 12 could possibly be used. Here, FIG. 11 is an external perspective view of the heat source unit 1 a (the fan grill having been removed), and FIG. 12 is a side view of the heat source unit 1 a with the right plate of the heat source unit 1 a having been removed. The terms “left” and “right” in the following description refer to a case of viewing the heat source unit 1 a from the side of the front plate.

The heat source unit 1 a constituting the air-conditioning apparatus 1 of the present modification is a so-called upward-blowing type in which air is drawn in from the sides and the air is blown upwards, the heat source unit 1 a having primarily a casing 71, and disposed inside the casing 71 a heat source-side heat exchanger 4, a intermediate heat exchanger 7, and other refrigerant circuit structural components, and/or a heat source-side fan 40 and other devices.

In the present modification, the casing 71 is a substantially rectangular parallelepiped-shaped box, and is configured primarily from a top plate 72 constituting the top surface of the casing 71, a left plate 73 constituting the external peripheral surface of the casing 71, a right plate 74, a front plate 75, a rear plate 76, and a bottom plate 77. The top plate 72 is primarily a member constituting the top surface of the casing 71, and in the present modification is a plate-shaped member seen as a substantial rectangle in a plan view, an air-blowing opening 71 a being formed substantially in the middle. A fan grill 78 is provided to the top plate 72 so as to cover the air-blowing opening 71 a from above. The left plate 73 is primarily a member constituting the left surface of the casing 71, and in the present modification is plate-shaped member seen as a substantial rectangle in a side view, extending downward from the left edge of the top plate 72. Intake openings 73 a are formed throughout almost the entire left plate 73, except for the top part. The right plate 74 is primarily a member constituting the right surface of the casing 71, and in the present modification is a plate-shaped member seen as a substantial rectangle in a side view, extending downward from the right edge of the top plate 72. Intake openings 74 a are formed throughout almost the entire right plate 74, except for the top part. The front plate 75 is a member primarily constituting the front surface of the casing 71, and in the present modification is configured from a plate-shaped member seen as a substantial rectangle in a front view, disposed in sequence below the front edge of the top plate 72. The rear plate 76 is primarily a member constituting the rear surface of the casing 71, and in the present modification is configured from a plate-shaped member seen as a substantial rectangle in a front view, disposed in sequence below the rear edge of the top plate 72. Intake openings 76 a are formed throughout almost the entire rear plate 76, except for the top part. The bottom plate 77 is primarily a member constituting the bottom surface of the casing 71, and in the present modification is a plate-shaped member seen as a substantial rectangle in a plan view.

In the present modification, the intermediate heat exchanger 7 is integrated with the heat source-side heat exchanger 4 in a state of being disposed above the heat source-side heat exchanger 4, and is also disposed on top of the bottom plate 77. More specifically, the intermediate heat exchanger 7 is integrated with the heat source-side heat exchanger 4 due to sharing heat transfer fins. The integration of the heat source-side heat exchanger 4 and the intermediate heat exchanger 7 forms a heat exchanger panel seen as a substantial U shape in a plan view in the present modification, and this panel is disposed so as to face the intake openings 73 a, 74 a, 76 a. The heat source-side fan 40 is directed towards the air-blowing opening 71 a of the top plate 72, and is disposed on the top side of the integration of the heat source-side heat exchanger 4 and the intermediate heat exchanger 7 (i.e., the heat exchanger panel). In the present modification, the heat source-side fan 40 is an axial flow fan and is rotatably driven by a fan drive motor 40 a, whereby air as a heat source is drawn from the intake openings 73 a, 74 a, 76 a into the casing 71, and after passing through the heat source-side heat exchanger 4 and the intermediate heat exchanger 7, the air can be blown upwards from the air-blowing opening 71 a (refer to the arrows indicating the flow of air in FIG. 12). Specifically, the heat source-side fan 40 is designed so as to supply air as a heat source to both the heat source-side heat exchanger 4 and the intermediate heat exchanger 7. The external shape of the heat source unit 1 a and/or the shape of the integration of the heat source-side heat exchanger 4 and intermediate heat exchanger 7 (i.e., the heat exchanger panel) are not limited to those described above. Thus, the intermediate heat exchanger 7 constitutes a heat exchanger panel integrated with the heat source-side heat exchanger 4, and the intermediate heat exchanger 7 is disposed in the top part of the heat exchanger panel.

The intermediate heat exchanger 7 and the heat source-side heat exchanger 4 are integrated and the intermediate heat exchanger 7 is disposed in the top part of the heat exchanger panel consisting of the two integrated heat exchangers in light of the fact that the air-conditioning apparatus 1 of the present modification uses a refrigerant that operates in a supercritical range (carbon dioxide in this case), and also the fact that the heat source unit 1 a is a model that draws air in from the sides and blows the air upward. To describe these facts in detail, sometimes the refrigeration cycle of the air-cooling operation, for example, is performed (see FIG. 3) in which refrigerant of an intermediate pressure lower than the critical pressure Pcp (approximately 7.3 MPa with carbon dioxide) flows into the intermediate heat exchanger 7 as a cooler during the air-cooling operation, and refrigerant of a high pressure exceeding the critical pressure Pcp flows into the heat source-side heat exchanger 4 functioning as a refrigerant radiator. In this case, as a result of the difference between the properties of the refrigerant at a pressure lower than the critical pressure Pcp and the properties (particularly the heat transfer coefficient and the specific heat at constant pressure) of the refrigerant at a pressure exceeding the critical pressure Pcp, there is a tendency for the heat transfer coefficient of the refrigerant in the intermediate heat exchanger 7 as a cooler to be lower than the heat transfer coefficient of the refrigerant in the heat source-side heat exchanger 4 functioning as a refrigerant radiator, as shown in FIG. 13. Here, FIG. 13 shows the heat transfer coefficient value (corresponding to the heat transfer coefficient of the refrigerant in the intermediate heat exchanger 7 as a cooler) in a case in which carbon dioxide at 6.5 MPa flows at a predetermined mass flow rate into a heat transfer passage having a predetermined passage cross-sectional surface area, as well as the heat transfer coefficient value (corresponding to the heat transfer coefficient of the refrigerant in the heat source-side heat exchanger 4 as a radiator) of carbon dioxide at 10 MPa in the same heat transfer passage and under the same mass flow rate conditions as the 6.5 MPa carbon dioxide. It is clear from this diagram that in the temperature range (35 to 70 degrees) of the refrigerant flowing within the heat source-side heat exchanger 4 functioning as a refrigerant radiator and/or the intermediate heat exchanger 7 functioning as a cooler of refrigerant, the heat transfer coefficient value of the 6.5 MPa carbon dioxide will be less than the heat transfer coefficient value of the 10 MPa carbon dioxide. Therefore, in the heat source unit 1 a of the air-conditioning apparatus 1 of the present modification (i.e., in a heat source unit configured so as to take air in from the sides and blow air upwards), when the intermediate heat exchanger 7 is tentatively integrated with the heat source-side heat exchanger 4 in a state of being disposed below the heat source-side heat exchanger 4, the intermediate heat exchanger 7 integrated with the heat source-side heat exchanger 4 is disposed in the bottom part of the heat source unit 1 a where the flow rate of air as the heat source is low, and the effects of the reduction in the heat transfer coefficient of the air in the intermediate heat exchanger 7 caused by disposing the intermediate heat exchanger 7 in the bottom part of the heat source unit 1 a combine with the effects of the heat transfer coefficient of the refrigerant in the intermediate heat exchanger 7 being lower than the heat transfer coefficient of the refrigerant in the heat source-side heat exchanger 4, which is because there is a reduction in the heat transfer performance of the intermediate heat exchanger 7.

In this type of heat source unit 1 a, if the intermediate heat exchanger bypass tube 9 were to be used during the air-warming operation so that the refrigerant discharged from the first-stage compression element 2 c and drawn into the second-stage compression element 2 d bypasses the intermediate heat exchanger 7 so as not to be cooled therein and the intermediate heat exchanger 7 is not used, there would be a severe disadvantage in that the intermediate heat exchanger 7, which is disposed in a position where the flow rate of air as a heat source is fastest in light of the heat transfer coefficient during the air-cooling operation, would not contribute at all during the air-warming operation, and the intermediate heat exchanger 7 would not be effectively used.

However, during the air-warming operation in the present modification, as in the above-described embodiment and the modification thereof, the intermediate heat exchanger bypass tube 9 is used so that the refrigerant discharged from the first-stage compression element 2 c and drawn into the second-stage compression element 2 d bypasses the intermediate heat exchanger 7 so as not to be cooled therein, and the intermediate heat exchanger 7 is made to function as an evaporator of refrigerant, thereby contributing to improving the evaporation capacity during the air-warming operation.

(5) Modification 3

In the above-described embodiment and the modifications thereof, the air-conditioning apparatus 1 which is configured to be capable of switching between the air-cooling operation and the air-warming operation via the switching mechanism 3 and which performs a two-stage compression refrigeration cycle is provided with an intermediate heat exchanger 7 that functions as a cooler of the refrigerant discharged from the first-stage compression element 2 c and drawn into the second-stage compression element 2 d, an intermediate heat exchanger bypass tube 9 connected to the intermediate refrigerant tube 8 so as to bypass the intermediate heat exchanger 7, a second intake return tube 92 for connecting one end of the intermediate heat exchanger 7 and the intake side of the compression mechanism 2, and an intermediate heat exchanger return tube 94 for connecting the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4 with the other end of the intermediate heat exchanger 7, but in addition to this configuration, intermediate pressure injection may be performed by a first second-stage injection tube 19 and an economizer heat exchanger 20.

For example, the refrigerant circuit 10 (see FIG. 1) of the above-described embodiment in which the two-stage compression-type compression mechanism 2 is used can be replaced by a refrigerant circuit 210 provided with the first second-stage injection tube 19 and the economizer heat exchanger 20, as shown in FIG. 14.

The first second-stage injection tube 19 has a function for branching off and returning the refrigerant flowing between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6 to the second-stage compression element 2 d of the compression mechanism 2. In the present modification, the first second-stage injection tube 19 is provided so as to branch off refrigerant flowing through the receiver inlet tube 18 a and return the refrigerant to the second-stage compression element 2 d. More specifically, the first second-stage injection tube 19 is provided so as to branch off refrigerant from a position upstream of the first expansion mechanism 5 a of the receiver inlet tube 18 a (i.e., a position between the heat source-side heat exchanger 4 and the first expansion mechanism 5 a when the switching mechanism 3 is set to the cooling operation state) and return the refrigerant to a position in the intermediate refrigerant tube 8 downstream of the intermediate heat exchanger 7. The first second-stage injection tube 19 is provided with a first second-stage injection valve 19 a whose opening degree can be controlled. The first second-stage injection valve 19 a is an electrically driven expansion valve in the present modification.

The economizer heat exchanger 20 is a heat exchanger for carrying out heat exchange between the refrigerant flowing between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6 and the refrigerant that flows through the first second stage injection tube 19 (more specifically, the refrigerant that has been depressurized to a nearly intermediate pressure in the first second-stage injection valve 19 a). In the present modification, the economizer heat exchanger 20 is provided so as to perform heat exchange between the refrigerant flowing through a position in the receiver inlet tube 18 a upstream of the first expansion mechanism 5 a (i.e., between the heat source-side heat exchanger 4 and the first expansion mechanism 5 a when the switching mechanism 3 is set to the cooling operation state) and the refrigerant flowing through the first second-stage injection tube 19, and the economizer heat exchanger 20 has a flow passage through which both refrigerants flow against each other. In the present modification, the economizer heat exchanger 20 is provided farther downstream than the position where the first second-stage injection tube 19 branches from the receiver inlet tube 18 a. Therefore, the refrigerant flowing between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6 is branched off in the receiver inlet tube 18 a into the first second-stage injection tube 19 before undergoing heat exchange in the economizer heat exchanger 20, and heat exchange is then conducted in the economizer heat exchanger 20 with the refrigerant flowing through the first second-stage injection tube 19.

Thus, in the present modification, when the switching mechanism 3 is set to the cooling operation state, the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 can be fed to the usage-side heat exchanger 6 through the inlet non-return valve 17 a of the bridge circuit 17, the economizer heat exchanger 20, the first expansion mechanism 5 a of the receiver inlet tube 18 a, the receiver 18, the second expansion mechanism 5 b of the receiver outlet tube 18 b, and the outlet non-return valve 17 c of the bridge circuit 17. When the switching mechanism 3 is brought to the heating operation state, the high-pressure refrigerant cooled in the usage-side heat exchanger 6 can be fed to the heat source-side heat exchanger 4 through the inlet non-return valve 17 b of the bridge circuit 17, the economizer heat exchanger 20, the first expansion mechanism 5 a of the receiver inlet tube 18 a, the receiver 18, the second expansion mechanism 5 b of the receiver outlet tube 18 b, and the outlet non-return valve 17 d of the bridge circuit 17.

Furthermore, in the present modification, the intermediate refrigerant tube 8 or the compression mechanism 2 is provided with an intermediate pressure sensor 54 for detecting the pressure of the refrigerant that flows through the intermediate refrigerant tube 8. The outlet of the first second-stage injection tube 19 side of the economizer heat exchanger 20 is provided with an economizer outlet temperature sensor 55 for detecting the temperature of the refrigerant at the outlet of the first second-stage injection tube 19 side of the economizer heat exchanger 20.

Next, the action of the air-conditioning apparatus 1 of the present modification will be described using FIGS. 14 through 18. FIG. 15 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation, FIG. 16 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation, FIG. 17 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation, and FIG. 18 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation. This air-cooling start control is the same as that of the embodiment described above and is therefore not described herein. Operation control in the air-cooling operation and air-warming operation described below (including the air-cooling start control not described herein) is performed by the controller (not shown) in the embodiment described above. In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, E, and H in FIGS. 15 and 16, and the pressure at points D, D′, F, and H in FIGS. 17 and 18), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A and F in FIGS. 15 and 16, and the pressure at points A, E, V in FIGS. 17 and 18), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1, C1, G, J, and K in FIGS. 15 through 18).

<Air-Cooling Operation>

During the air-cooling operation, the switching mechanism 3 is brought to the cooling operation state shown by the solid lines in FIG. 14. The opening degrees of the first expansion mechanism 5 a and the second expansion mechanism 5 b are adjusted. Furthermore, the opening degree of the first second-stage injection valve 19 a is also adjusted. More specifically, in the present modification, what is known as superheat degree control is performed, wherein the opening degree of the first second-stage injection valve 19 a is adjusted so that a target value is achieved in the degree of superheat of the refrigerant at the outlet in the first second-stage injection tube 19 side of the economizer heat exchanger 20. In the present modification, the degree of superheat of the refrigerant at the outlet in the first second-stage injection tube 19 side of the economizer heat exchanger 20 is obtained by converting the intermediate pressure detected by the intermediate pressure sensor 54 to a saturation temperature and subtracting this refrigerant saturation temperature value from the refrigerant temperature detected by the economizer outlet temperature sensor 55. Though not used in the present modification, another possible option is to provide a temperature sensor to the inlet in the first second-stage injection tube 19 side of the economizer heat exchanger 20, and to obtain the degree of superheat of the refrigerant at the outlet in the first second-stage injection tube 19 side of the economizer heat exchanger 20 by subtracting the refrigerant temperature detected by this temperature sensor from the refrigerant temperature detected by the economizer outlet temperature sensor 55. Adjusting the opening degree of the first second-stage injection valve 19 a is not limited to the superheat degree control, and the valve may be opened to predetermined opening degree in accordance with the flow rate of refrigerant circulating in the refrigerant circuit 10, for example. Since the switching mechanism 3 is set to the cooling operation state, a state in which the intermediate heat exchanger 7 functions as a cooler is created by opening the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 and closing the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9, a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected is created (except during air-cooling start control) by closing the second intake return on/off valve 92 a of the second intake return tube 92, and a state in which the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4 is not connected with the intermediate heat exchanger 7 is created by closing the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94.

When the refrigerant circuit 210 is in this state, low-pressure refrigerant (refer to point A in FIGS. 14 through 16) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 14 through 16). The intermediate-pressure refrigerant discharged from the first-stage compression element 2 c is cooled by heat exchange with water or air as a cooling source in the intermediate heat exchanger 7 (refer to point C1 in FIGS. 14 to 16). The refrigerant cooled in the intermediate heat exchanger 7 is further cooled (refer to point G in FIGS. 14 to 16) by being mixed with refrigerant being returned from the first second-stage injection tube 19 to the second-stage compression element 2 d (refer to point K in FIGS. 14 to 16). Next, having been mixed with the refrigerant returning from the first second-stage injection tube 19 (i.e., intermediate pressure injection is carried out by the economizer heat exchanger 20), the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 14 through 16). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 15). The high-pressure refrigerant discharged from the compression mechanism 2 flows into the oil separator 41 a constituting the oil separation mechanism 41, and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in the oil separator 41 a flows into the oil return tube 41 b constituting the oil separation mechanism 41 wherein it is depressurized by the pressure-reducing mechanism 41 c provided to the oil return tube 41 b, and the oil is then returned to the intake tube 2 a of the compression mechanism 2 and drawn back into the compression mechanism 2. Next, having been separated from the refrigeration oil in the oil separation mechanism 41, the high-pressure refrigerant is passed through the non-return mechanism 42 and the switching mechanism 3, and is fed to the heat source-side heat exchanger 4 functioning as a refrigerant radiator. The high-pressure refrigerant fed to the heat source-side heat exchanger 4 is cooled in the heat source-side heat exchanger 4 by heat exchange with water or air as a cooling source (refer to point E in FIGS. 14 through 16). The high-pressure refrigerant cooled in the heat source-side heat exchanger 4 flows through the inlet non-return valve 17 a of the bridge circuit 17 into the receiver inlet tube 18 a, and some of the refrigerant is branched off into the first second-stage injection tube 19. The refrigerant flowing through the first second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the first second-stage injection valve 19 a and is then fed to the economizer heat exchanger 20 (refer to point J in FIGS. 14 to 16). The refrigerant branched off to the first second-stage injection tube 19 then flows into the economizer heat exchanger 20, where it is cooled by heat exchange with the refrigerant flowing through the first second-stage injection tube 19 (refer to point H in FIGS. 14 to 16). The refrigerant flowing through the first second-stage injection tube 19 is heated by heat exchange with the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator (refer to point K in FIGS. 14 through 16), and is then mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The high-pressure refrigerant cooled in the economizer heat exchanger 20 is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I in FIG. 14). The refrigerant retained in the receiver 18 is fed to the receiver outlet tube 18 b and is depressurized by the second expansion mechanism 5 b to become a low-pressure gas-liquid two-phase refrigerant, and is then fed through the outlet non-return valve 17 c of the bridge circuit 17 to the usage-side heat exchanger 6 functioning as a refrigerant evaporator (refer to point F in FIGS. 14 to 16). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchanger 6 is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A in FIGS. 14 to 16). The low-pressure refrigerant heated in the usage-side heat exchanger 6 is then drawn back into the compression mechanism 2 via the switching mechanism 3. In this manner the air-cooling operation is performed.

In the configuration of the present modification, as in Modification 2 described above, since the intermediate heat exchanger 7 is in a state of functioning as a cooler during the air-cooling operation in which the switching mechanism 3 is brought to the cooling operation state, heat radiation loss in the heat source-side heat exchanger 4 can be reduced in comparison with cases in which no intermediate heat exchanger 7 is provided.

Moreover, in the configuration of the present modification, since the first second-stage injection tube 19 and the economizer heat exchanger 20 are provided so as to branch off refrigerant fed from the heat source-side heat exchanger 4 to the expansion mechanisms 5 a, 5 b and return the refrigerant to the second-stage compression element 2 d, the temperature of refrigerant drawn into the second-stage compression element 2 d can be kept even lower (refer to points C1 and G in FIG. 16) without performing heat radiation to the exterior, such as is done with the intermediate heat exchanger 7. The temperature of the refrigerant discharged from the compression mechanism 2 is thereby kept even lower (refer to points D and D′ in FIG. 16), and operating efficiency can be further improved because heat radiation loss can be further reduced in proportion to the area enclosed by connecting the points C1, D′, D, and G in FIG. 16, in comparison with cases in which no first second-stage injection tube 19 is provided.

In the present modification, as in Modification 2 described above, at the start of the air-cooling operation in which the switching mechanism 3 is set to the cooling operation state, the refrigerant discharged from the first-stage compression element 2 c is drawn into the second-stage compression element 2 d through the intermediate heat exchanger bypass tube 9, and the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected through the second intake return tube 92. Therefore, even if liquid refrigerant has accumulated in the intermediate heat exchanger 7 prior to the start of the operation in which the switching mechanism 3 is set to the cooling operation state, the liquid refrigerant can be removed from the intermediate heat exchanger 7. Thereby, at the start of the operation in which the switching mechanism 3 is set to the cooling operation state, it is possible to avoid a state of liquid refrigerant accumulating inside the intermediate heat exchanger 7, liquid compression does not occur in the second-stage compression element 2 d as a result of liquid refrigerant accumulating in the intermediate heat exchanger 7, and the reliability of the compression mechanism 2 can be improved.

<Air-Warming Operation>

During the air-warming operation, the switching mechanism 3 is brought to the heating operation state shown by the dashed lines in FIG. 14. The opening degrees of the first expansion mechanism 5 a and the second expansion mechanism 5 b are adjusted. The first second-stage injection valve 19 a is also subjected to the same opening degree adjustment as in the air-cooling operation described above. Since the switching mechanism 3 is set to the heating operation state, the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 is closed and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is opened, thereby putting the intermediate heat exchanger 7 into a state of not functioning as a cooler. Furthermore, since the switching mechanism 3 is in the heating operation state, a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected is created by opening the second intake return on/off valve 92 a of the second intake return tube 92, and a state in which the portion between the usage-side heat exchanger 6 and the heat source-side heat exchanger 4 is connected with the intermediate heat exchanger 7 is created by opening the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94.

When the refrigerant circuit 210 is in this state, low-pressure refrigerant (refer to point A in FIGS. 14, 17, and 18) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 14, 17, 18). Unlike in the air-cooling operation, the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c passes through the intermediate heat exchanger bypass tube 9 (refer to point C1 in FIGS. 14, 17, and 18) without passing through the intermediate heat exchanger 7 (i.e., without being cooled), and the refrigerant is cooled (refer to point G in FIGS. 14, 17, and 18) by being mixed with refrigerant being returned from the first second-stage injection tube 19 to the second-stage compression element 2 d (refer to point K in FIGS. 14, 17, and 18). Next, having been mixed with the refrigerant returning from the first second-stage injection tube 19, the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 14, 17, and 18). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 17), similar to the air-cooling operation. The high-pressure refrigerant discharged from the compression mechanism 2 flows into the oil separator 41 a constituting the oil separation mechanism 41, and the accompanying refrigeration oil is separated. The refrigeration oil separated from the high-pressure refrigerant in the oil separator 41 a flows into the oil return tube 41 b constituting the oil separation mechanism 41 wherein it is depressurized by the pressure-reducing mechanism 41 c provided to the oil return tube 41 b, and the oil is then returned to the intake tube 2 a of the compression mechanism 2 and drawn back into the compression mechanism 2. Next, after the refrigeration oil has been separated in the oil separation mechanism 41, the high-pressure refrigerant is fed through the non-return mechanism 42 and the switching mechanism 3 to the usage-side heat exchanger 6 functioning as a refrigerant radiator, and is cooled by heat exchange with water and/or air as a cooling source (refer to point F in FIGS. 14, 17, and 18). The high-pressure refrigerant cooled in the usage-side heat exchanger 6 flows through the inlet non-return valve 17 b of the bridge circuit 17 into the receiver inlet tube 18 a, and some of the refrigerant is branched off into the first second-stage injection tube 19. The refrigerant flowing through the first second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the first second-stage injection valve 19 a and is then fed to the economizer heat exchanger 20 (refer to point J in FIGS. 14, 17, and 18). The refrigerant branched off to the first second-stage injection tube 19 then flows into the economizer heat exchanger 20, where it is cooled by heat exchange with the refrigerant flowing through the first second-stage injection tube 19 (refer to point H in FIGS. 14, 17, and 18). The refrigerant flowing through the first second-stage injection tube 19 is heated by heat exchange with the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator (refer to point K in FIGS. 14, 17, and 18), and is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The high-pressure refrigerant cooled in the economizer heat exchanger 20 is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I in FIG. 14). The refrigerant retained in the receiver 18 is then fed to the receiver outlet tube 18 b and depressurized by the second expansion mechanism 5 b to become low-pressure gas-liquid two-phase refrigerant, which is then fed through the outlet non-return valve 17 d of the bridge circuit 17 to the heat source-side heat exchanger 4 functioning as an evaporator of refrigerant, and is also fed through the intermediate heat exchanger return tube 94 to the intermediate heat exchanger 7 functioning as an evaporator of refrigerant (refer to point E in FIGS. 14, 17, and 18). The low-pressure gas-liquid two-phase refrigerant fed to the heat source-side heat exchanger 4 is heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point A in FIGS. 14, 17, and 18). The low-pressure gas-liquid two-phase refrigerant fed to the intermediate heat exchanger 7 is also heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point V in FIGS. 14, 17, and 18). The low-pressure refrigerant heated and evaporated in the heat source-side heat exchanger 4 is then drawn back into the compression mechanism 2 via the switching mechanism 3. The low-pressure refrigerant heated and evaporated in the intermediate heat exchanger 7 is then drawn back into the compression mechanism 2 via the second intake return tube 92. In this manner the air-warming operation is performed.

In the configuration of the present modification, as in Modification 2 described above, during the air-warming operation in which the switching mechanism 3 is set to the heating operation state, heat radiation to the exterior can be minimized, the decrease of heating capacity can be minimized, and decreases in operating efficiency can be prevented in comparison with cases in which only the intermediate heat exchanger 7 is provided and/or cases in which the intermediate heat exchanger 7 is made to function as a cooler, similar to the air-cooling operation described above.

Moreover, in the configuration of the present modification, since the first second-stage injection tube 19 and the economizer heat exchanger 20 are provided so as to branch off refrigerant fed from the heat source-side heat exchanger 4 to the expansion mechanisms 5 a, 5 b and return the refrigerant to the second-stage compression element 2 d in the same manner as the air-cooling operation, the temperature of refrigerant drawn into the second-stage compression element 2 d can be kept even lower (refer to points B1 and G in FIG. 18) without performing heat radiation to the exterior, such as is done with the intermediate heat exchanger 7. The temperature of refrigerant discharged from the compression mechanism 2 is thereby kept even lower (refer to points D and D′ in FIG. 18), and operating efficiency can be further improved because heat radiation loss can be reduced in proportion to the area enclosed by connecting the points B1, D′, D, and G in FIG. 18, in comparison with cases in which no first second-stage injection tube 19 is provided.

In the configuration of the present modification, similar to the embodiment described above, during the air-cooling operation, there is less heat radiation loss in the heat source-side heat exchanger 4 functioning as a refrigerant radiator, and the operating efficiency during the air-cooling operation can be improved. During the air-warming operation, it is possible to effectively use the intermediate heat exchanger 7, minimize the loss of heating capacity in the usage-side heat exchanger 6, and prevent the operating efficiency during the air-warming operation from decreasing.

Advantages of both the air-cooling operation and the air-warming operation in the configuration of the present modification are that the economizer heat exchanger 20 is a heat exchanger which has flow channels through which refrigerant fed from the heat source-side heat exchanger 4 or usage-side heat exchanger 6 to the expansion mechanisms 5 a, 5 b and refrigerant flowing through the second-stage injection tube 19 both flow so as to oppose each other; therefore, it is possible to reduce the temperature difference between the refrigerant fed to the expansion mechanisms 5 a, 5 b from the heat source-side heat exchanger 4 or the usage-side heat exchanger 6 in the economizer heat exchanger 20 and the refrigerant flowing through the second-stage injection tube 19, and high heat exchange efficiency can be obtained.

In the present modification, switching between the air-cooling operation and the air-cooling start control, i.e., switching between the refrigerant non-return state and the refrigerant return state is performed through the on/off states of the on/off valves 11, 12, 92 a, but another option instead of the on/off valves 11, 12, 92 a is to provide an intermediate heat exchanger switching valve 93 capable of switching between the refrigerant non-return state and the refrigerant return state, as in Modification 1 described above.

Furthermore, particularly advantageous effects can be obtained when using the configuration of the heat source unit 1 a, such as the one in Modification 2.

(6) Modification 4

In the refrigerant circuit 210 (see FIG. 14) in Modification 3 described above, in both the air-cooling operation in which the switching mechanism 3 is set to the cooling operation state and the air-warming operation in which the switching mechanism 3 is set to the heating operation state as described above, performing intermediate pressure injection through the economizer heat exchanger 20 reduces the temperature of the refrigerant discharged from the second-stage compression element 2 d, reduces the power consumption of the compression mechanism 2, and makes it possible to improve operating efficiency. Intermediate pressure injection by the economizer heat exchanger 20 can be used in conditions in which the intermediate pressure in the refrigeration cycle has increased to a nearly critical pressure, which is believed to be particularly advantageous in cases in which refrigerant that operates in a supercritical range is used with a configuration having a single usage-side heat exchanger 6, such as the refrigerant circuits 10, 110, 210 (see FIGS. 1, 10, and 14) in the above-described embodiment and the modifications thereof.

However, in order to create a configuration having a plurality of usage-side heat exchangers 6 connected in parallel to each other, and to make it possible to control the flow rate of refrigerant flowing through the usage-side heat exchangers 6 and obtain the refrigeration load required by the usage-side heat exchangers 6, the objective being to perform air-cooling or air-warming corresponding to the air-conditioning loads of a plurality of air-conditioned spaces, for example; in some cases usage-side expansion mechanisms 5 c are provided between the receiver 18 as a gas-liquid separator and the usage-side heat exchangers 6 so as to correspond to the usage-side heat exchangers 6.

For example, although the details are not shown, one possibility in the refrigerant circuit 210 (see FIG. 14) having the bridge circuit 17 in Modification 3 described above is that a plurality (two herein) of usage-side heat exchangers 6 connected to each other in parallel be provided, usage-side expansion mechanisms 5 c (see FIG. 19) be provided between the receiver 18 as a gas-liquid separator (more specifically, the bridge circuit 17) and the usage-side heat exchangers 6 so as to correspond to the usage-side heat exchangers 6, the second expansion mechanism 5 b that has been provided to the receiver outlet tube 18 b be omitted, and a third expansion mechanism for depressurizing the refrigerant to a low pressure in the refrigeration cycle during the air-warming operation be provided instead of the outlet non-return valve 17 d of the bridge circuit 17.

In this type of configuration as well, the intermediate pressure injection by the economizer heat exchanger 20 is advantageous similar to Modification 3 described above, under the condition that the pressure difference between the high pressure in the refrigeration cycle and the nearly intermediate pressure of the refrigeration cycle can be used without performing a severe depressurizing operation everywhere but the first expansion mechanism 5 a as a heat source-side expansion mechanism after cooling takes place in the heat source-side heat exchanger 4 as a radiator, as is the case in the air-cooling operation in which the switching mechanism 3 is set to the cooling operation state.

However, in conditions such as those of the air-warming operation for setting the switching mechanism 3 to the heating operation state, the usage-side expansion mechanisms 5 c control the flow rate of refrigerant flowing through the usage-side heat exchangers 6 as radiators so as to obtain the refrigeration loads required by the usage-side heat exchangers 6 as radiators, and the flow rate of refrigerant passing through the usage-side heat exchangers 6 as radiators is established for the most part by the operation of depressurizing the refrigerant by controlling the opening degrees of the usage-side expansion mechanisms 5 c provided downstream of the usage-side heat exchangers 6 as radiators and upstream of the economizer heat exchanger 20. Under such conditions, the extent of refrigerant depressurization by controlling the opening degrees of the usage-side expansion mechanisms 5 c fluctuates not only due to the flow rate of refrigerant flowing through the usage-side heat exchangers 6 as radiators, but also due to the state of flow rate distribution among the plurality of usage-side heat exchangers 6 as radiators, and there are cases in which the extent of depressurization differs greatly among the plurality of usage-side expansion mechanisms 5 c, or the extent of depressurization in the usage-side expansion mechanisms 5 c is comparatively large. Therefore, there is a risk of a decrease in the refrigerant pressure in the inlet of the economizer heat exchanger 20, and in such cases there is a risk that the quantity of heat exchanged in the economizer heat exchanger 20 (i.e., the flow rate of refrigerant flowing through the first second-stage injection tube 19) will decrease and usage will be difficult. Particularly in cases in which this type of air-conditioning apparatus 1 is configured as a separate-type air-conditioning apparatus in which a heat source unit including primarily a compression mechanism 2, a heat source-side heat exchanger 4, and a receiver 18 is connected by communication pipe with a usage unit including primarily a usage-side heat exchanger 6, the communication pipe might be extremely long depending on the arrangement of the usage unit and the heat source unit; therefore, in addition to the effects of pressure drop, the pressure of the refrigerant in the inlet of the economizer heat exchanger 20 further decreases. In cases in which there is a risk of a decrease in the pressure of the refrigerant in the inlet of the economizer heat exchanger 20, if the gas-liquid separator pressure is lower than the critical pressure, intermediate pressure injection by a useable gas-liquid separator is still advantageous even under conditions in which there is a small difference in pressure between the gas-liquid separator pressure and the intermediate pressure in the refrigeration cycle (here, the pressure of the refrigerant flowing through the intermediate refrigerant tube 8).

In view of this, in the present modification as shown in FIG. 19, to enable the receiver 18 to function as a gas-liquid separator and to enable intermediate pressure injection to be performed, a refrigerant circuit 310 is used in which a second second-stage injection tube 18 c is connected to the receiver 18, intermediate pressure injection can be performed by the economizer heat exchanger 20 during the air-cooling operation, and intermediate pressure injection can be performed by the receiver 18 as a gas-liquid separator during the air-warming operation.

The second second-stage injection tube 18 c is a refrigerant tube capable of performing intermediate pressure injection for removing refrigerant from the receiver 18 and returning the refrigerant to the second-stage compression element 2 d of the compression mechanism 2, and in the present modification, the second second-stage injection tube 18 c is provided so as to connect the top part of the receiver 18 and the intermediate refrigerant tube 8 (i.e., the intake side of the second-stage compression element 2 d of the compression mechanism 2). The second second-stage injection tube 18 c is provided with a second second-stage injection on/off valve 18 d and a second second-stage injection non-return mechanism 18 e. The second second-stage injection on/off valve 18 d is a valve capable of opening and closing, and is an electromagnetic valve in the present modification. The second second-stage injection non-return mechanism 18 e is a mechanism for allowing refrigerant to flow from the receiver 18 to the second-stage compression element 2 d and blocking refrigerant from flowing from the second-stage compression element 2 d to the receiver 18, and a non-return valve is used in the present modification. The second second-stage injection tube 18 c and the first intake return tube 18 f are integrated in a portion near the receiver 18. The second second-stage injection tube 18 c and the first second-stage injection tube 19 are integrated in a portion near the intermediate refrigerant tube 8. In the present modification, the usage-side expansion mechanisms 5 c are electrically driven expansion valves. In the present modification, as described above, the first second-stage injection tube 19 and the economizer heat exchanger 20 are used during the air-cooling operation, and the second second-stage injection tube 18 c is used during the air-warming operation; therefore, since there is no need for the direction of refrigerant flow to the economizer heat exchanger 20 to be constant for both the air-cooling operation and the air-warming operation, the bridge circuit 17 is omitted and the configuration of the refrigerant circuit 310 is simplified.

Next, the action of the air-conditioning apparatus 1 of the present modification will be described using FIGS. 19, 15, 16, 20, and 21. FIG. 20 is a pressure-enthalpy graph representing the refrigeration cycle during the air-warming operation, and FIG. 21 is a temperature-entropy graph representing the refrigeration cycle during the air-warming operation. This air-cooling start control is the same as that of the embodiment described above and is therefore not described herein. The refrigeration cycle during the air-cooling operation in the present modification is described using FIGS. 15 and 16. Operation control (including air-cooling start control not described herein) in the following air-cooling operation and air-warming operation is performed by the controller (not shown) in the embodiment described above. In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, D′, E, and H in FIGS. 15 and 16, and the pressure at points D, D′, and F in FIGS. 20 and 21), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A and F in FIGS. 15 and 16, and the pressure at points A, E, and V in FIGS. 20 and 21), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1, C1, G, J, and K in FIGS. 15 and 16, and the pressure at points B1, C1, G, I, L, and M in FIGS. 20 and 21).

<Air-Cooling Operation>

During the air-cooling operation, the switching mechanism 3 is brought to the cooling operation state shown by the solid lines in FIG. 19. The opening degrees of the first expansion mechanism 5 a and the usage-side expansion mechanisms 5 c as heat source-side expansion mechanisms are adjusted. Since the switching mechanism 3 is in the cooling operation state, opening the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 and closing the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 creates a state in which the intermediate heat exchanger 7 functions as a cooler, closing the second intake return on/off valve 92 a of the second intake return tube 92 creates a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected (except during air-cooling start control), and closing the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 creates a state in which the portion between the usage-side heat exchangers 6 and the heat source-side heat exchanger 4 is not connected with the intermediate heat exchanger 7. When the switching mechanism 3 has been set to the cooling operation state, intermediate pressure injection is not performed by the receiver 18 as a gas-liquid separator, but instead intermediate pressure injection is performed by the economizer heat exchanger 20 for returning the refrigerant heated in the economizer heat exchanger 20 to the second-stage compression element 2 d through the first second-stage injection tube 19. More specifically, the second second-stage injection on/off valve 18 d is closed, and the opening degree of the first second-stage injection valve 19 a is adjusted in the same manner as Modification 3 described above.

When the refrigerant circuit 310 is in this state, low-pressure refrigerant (refer to point A in FIGS. 19, 15, and 16) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 19, 15, 16). The intermediate-pressure refrigerant discharged from the first-stage compression element 2 c is cooled by heat exchange with water or air as a cooling source in the intermediate heat exchanger 7 (refer to point C1 in FIGS. 19, 15, and 16). The refrigerant cooled in the intermediate heat exchanger 7 is further cooled (refer to point G in FIGS. 19, 15, and 16) by being mixed with refrigerant being returned from the first second-stage injection tube 19 to the second-stage compression element 2 d (refer to point K in FIGS. 19, 15, and 16). Next, having been mixed with the refrigerant returning from the first second-stage injection tube 19 (i.e., intermediate pressure injection is carried out by the economizer heat exchanger 20), the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 19, 15, and 16). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 15). The high-pressure refrigerant discharged from the compression mechanism 2 is fed via the switching mechanism 3 to the heat source-side heat exchanger 4 functioning as a refrigerant radiator, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point E in FIGS. 19, 15, and 16). Some of the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator is then branched off to the first second-stage injection tube 19. The refrigerant flowing through the first second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the first second-stage injection valve 19 a and is then fed to the economizer heat exchanger 20 (refer to point J in FIGS. 19, 15, and 16). The refrigerant branched off to the first second-stage injection tube 19 then flows into the economizer heat exchanger 20, where it is cooled by heat exchange with the refrigerant flowing through the first second-stage injection tube 19 (refer to point H in FIGS. 19, 15, and 16). The refrigerant flowing through the first second-stage injection tube 19 is heated by heat exchange with the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator (refer to point K in FIGS. 19, 15, and 16), and is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The high-pressure refrigerant cooled in the economizer heat exchanger 20 is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I in FIGS. 19, 15, and 16). The refrigerant retained in the receiver 18 is then fed to the usage-side expansion mechanisms 5 c and depressurized by the usage-side expansion mechanisms 5 c to become a low-pressure gas-liquid two-phase refrigerant, which is fed to the usage-side heat exchangers 6 functioning as evaporators of refrigerant (refer to point F in FIGS. 19, 15, and 16). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchangers 6 that function as evaporators is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A in FIGS. 19, 15, and 16). The low-pressure refrigerant heated and evaporated in the usage-side heat exchangers 6 that function evaporators is then drawn back into the compression mechanism 2 via the switching mechanism 3. In this manner the air-cooling operation is performed.

<Air-Warming Operation>

During the air-warming operation, the switching mechanism 3 is brought to the heating operation state shown by the dashed lines in FIG. 19. The opening degrees of the first expansion mechanism 5 a and the usage-side expansion mechanisms 5 c as heat source-side expansion mechanisms are adjusted. Since the switching mechanism 3 is set to the heating operation state, the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 is closed and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is opened, thereby putting the intermediate heat exchanger 7 into a state of not functioning as a cooler. Furthermore, since the switching mechanism 3 is in the heating operation state, opening the second intake return on/off valve 92 a of the second intake return tube 92 creates a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected, and opening the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 creates a state in which the portion between the usage-side heat exchangers 6 and the heat source-side heat exchanger 4 is connected with the intermediate heat exchanger 7. When the switching mechanism 3 has been set to the heating operation state, intermediate pressure injection is not performed by the economizer heat exchanger 20, but instead intermediate pressure injection is performed by the receiver 18 for returning the refrigerant from the receiver 18 as a gas-liquid separator to the second-stage compression element 2 d through the second second-stage injection tube 18 c. More specifically, the second second-stage injection on/off valve 18 d is opened, and the first second-stage injection valve 19 a is fully closed.

When the refrigerant circuit 310 is in this state, low-pressure refrigerant (refer to point A in FIGS. 19 through 21) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 19 through 21). Unlike during the air-cooling operation, the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c passes through the intermediate heat exchanger bypass tube 9 (refer to point C1 in FIGS. 19 to 21) without passing through the intermediate heat exchanger 7 (i.e., without being cooled), and is mixed with the refrigerant returning from the receiver 18 to the second-stage compression element 2 d through the second second-stage injection tube 18 c (refer to point M in FIGS. 19 to 21), thereby being cooled (refer to point G in FIGS. 19 to 21). Next, having been mixed with the refrigerant returning from the second second-stage injection tube 18 c (i.e., intermediate pressure injection is carried out by the receiver 18 which acts as a gas-liquid separator), the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 19 through 21). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 20), similar to the air-cooling operation. The high-pressure refrigerant discharged from the compression mechanism 2 is fed via the switching mechanism 3 to the usage-side heat exchangers 6 functioning as refrigerant radiators, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point F in FIGS. 19 to 21). The high-pressure refrigerant cooled in the usage-side heat exchangers 6 as radiators is then depressurized to a nearly intermediate pressure by the usage-side expansion mechanisms 5 c, and is then temporarily retained in the receiver 18 and subjected to gas-liquid separation (refer to points I, L, and M in FIGS. 19 to 21). The gas refrigerant after having undergone gas-liquid separation in the receiver 18 is then removed from the top part of the receiver 18 by the second second-stage injection tube 18 c, and is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The liquid refrigerant retained in the receiver 18 is depressurized by the first expansion mechanism 5 a to become a low-pressure gas-liquid two-phase refrigerant, which is fed to the heat source-side heat exchanger 4 functioning as an evaporator of refrigerant, and is also fed through the intermediate heat exchanger return tube 94 to the intermediate heat exchanger 7 functioning as an evaporator of refrigerant (refer to point E in FIGS. 19 to 21). The low-pressure gas-liquid two-phase refrigerant fed to the heat source-side heat exchanger 4 is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A in FIGS. 19 to 21). The low-pressure gas-liquid two-phase refrigerant fed to the intermediate heat exchanger 7 is also heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point V in FIGS. 19 through 21). The low-pressure refrigerant heated and evaporated in the heat source-side heat exchanger 4 is then drawn back into the compression mechanism 2 via the switching mechanism 3. The low-pressure refrigerant heated and evaporated in the intermediate heat exchanger 7 is then drawn back into the compression mechanism 2 via the second intake return tube 92. In this manner the air-warming operation is performed.

The configuration of the present modification is different from that of Modification 3 in that intermediate pressure injection is performed by the receiver 18 as a gas-liquid separator instead of intermediate pressure injection by the economizer heat exchanger 20 during the air-warming operation, but otherwise the same operational effects as those of Modification 3 can be obtained.

In the present modification, the switching between the air-cooling operation and air-cooling start control, i.e., the switching between the refrigerant non-return state and the refrigerant return state is performed by the on/off states of the on/off valves 11, 12, 92 a, but an intermediate heat exchanger switching valve 93 capable of switching between the refrigerant non-return state and the refrigerant return state may be provided instead of the on/off valves 11, 12, 92 a, as in Modification 1 described above.

Furthermore, particularly advantageous effects can be obtained when using the configuration of the heat source unit 1 a such as the one in Modification 2.

(7) Modification 5

The refrigerant circuit 310 (see FIG. 19) in Modification 4 described above comprises a configuration having a plurality of usage-side heat exchangers 6 connected to each other in parallel with the objective of performing air cooling and/or air warming according to the air-conditioning load of a plurality of air-conditioned spaces, for example, and also uses a configuration in which usage-side expansion mechanisms 5 c are provided between the receiver 18 and the usage-side heat exchangers 6 so as to correspond to the usage-side heat exchangers 6, in order to make it possible to control the flow rate of refrigerant flowing through the usage-side heat exchangers 6 and obtain the refrigeration load required by the usage-side heat exchangers 6. With this type of configuration, during the air-cooling operation, the refrigerant depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and temporarily retained in the receiver 18 (refer to point I in FIG. 19) is distributed among the usage-side expansion mechanisms 5 c, but when the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c is in a gas-liquid two-phase state, there is a risk of the flow being imbalanced when the refrigerant is distributed among the usage-side expansion mechanisms 5 c, and it is therefore preferable that the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c be brought as much as possible to a subcooled state.

In view of this, in the present modification, the refrigerant circuit 310 in Modification 4 described above is replaced by a refrigerant circuit 410 provided with a subcooling heat exchanger 96 and a third intake return tube 95 between the receiver 18 and the usage-side expansion mechanisms 5 c, as shown in FIG. 22.

The subcooling heat exchanger 96 is a heat exchanger for cooling the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c. More specifically, during the air-cooling operation, the subcooling heat exchanger 96 is a heat exchanger for performing heat exchange with the refrigerant flowing through the third intake return tube 95, which branches off some of the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c and returns the refrigerant to the intake side of the compression mechanism 2 (i.e., to the intake tube 2 a between the compression mechanism 2 and the usage-side heat exchangers 6 as evaporators), and the subcooling heat exchanger 96 has a flow passage through which both refrigerants flow against each other. The third intake return tube 95 herein is a refrigerant tube for branching off the refrigerant fed from the heat source-side heat exchanger 4 as a radiator to the usage-side expansion mechanisms 5 c and returning the refrigerant to the intake side of the compression mechanism 2 (i.e., the intake tube 2 a). The third intake return tube 95 is provided with a third intake return valve 95 a whose opening degree can be controlled, and in the subcooling heat exchanger 96, heat exchange is performed between the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c and the refrigerant flowing through the third intake return tube 95 after having been depressurized to a nearly low pressure in the third intake return valve 95 a. The intake return valve 95 a is an electrically driven expansion valve in the present modification. An intake pressure sensor 60 for detecting the pressure of the refrigerant flowing through the intake side of the compression mechanism 2 is provided to either the intake tube 2 a or the compression mechanism 2. The outlet of the subcooling heat exchanger 96 on the side near the third intake return tube 95 is provided with a subcooling heat exchange outlet temperature sensor 59 for detecting the temperature of the refrigerant in the outlet of the subcooling heat exchanger 96 on the side near the third intake return tube 95.

Next, the action of the air-conditioning apparatus 1 in the present modification will be described using FIGS. 22 to 24, 20, and 21. FIG. 23 is a pressure-enthalpy graph representing the refrigeration cycle during the air-cooling operation, and FIG. 24 is a temperature-entropy graph representing the refrigeration cycle during the air-cooling operation. This air-cooling start control is the same as that of the embodiment described above and is therefore not described herein. The refrigeration cycle during the air-warming operation in the present modification is described using FIGS. 20 and 21. Operation control during the following air-cooling operation and air-warming operation (including the air-cooling start control not described herein) is performed by the controller (not shown) in the embodiment described above. In the following description, the term “high pressure” means a high pressure in the refrigeration cycle (specifically, the pressure at points D, E, I, and R in FIGS. 23 and 24, and the pressure at points D, D′, and F in FIGS. 20 and 21), the term “low pressure” means a low pressure in the refrigeration cycle (specifically, the pressure at points A, F, F, S′, and U in FIGS. 23 and 24, and the pressure at points A, E, and V in FIGS. 20 and 21), and the term “intermediate pressure” means an intermediate pressure in the refrigeration cycle (specifically, the pressure at points B1, C1, G, J, and K in FIGS. 23 and 24, and the pressure at points B1, C1, G, I, L, and M in FIGS. 20 and 21).

<Air-Cooling Operation>

During the air-cooling operation, the switching mechanism 3 is brought to the cooling operation state shown by the solid lines in FIG. 22. The opening degrees of the first expansion mechanism 5 a and the usage-side expansion mechanisms 5 c as heat source-side expansion mechanisms are adjusted. Since the switching mechanism 3 is in the cooling operation state, opening the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 and closing the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 creates a state in which the intermediate heat exchanger 7 functions as a cooler, closing the second intake return on/off valve 92 a of the second intake return tube 92 creates a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are not connected (except during air-cooling start control), and closing the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 creates a state in which the portion between the usage-side heat exchangers 6 and the heat source-side heat exchanger 4 is not connected with the intermediate heat exchanger 7. When the switching mechanism 3 has been set to the cooling operation state, intermediate pressure injection is not performed by the receiver 18 as a gas-liquid separator, but instead intermediate pressure injection is performed by the economizer heat exchanger 20 for returning the refrigerant heated in the economizer heat exchanger 20 to the second-stage compression element 2 d through the first second-stage injection tube 19. More specifically, the second second-stage injection on/off valve 18 d is closed, and the opening degree of the first second-stage injection valve 19 a is adjusted in the same manner as Modification 3 described above. When the switching mechanism 3 is in the cooling operation state, the opening degree of the third intake return valve 95 a is also adjusted because the subcooling heat exchanger 96 is used. More specifically, in the present modification, what is known as superheat degree control is performed, wherein the opening degree of the third intake return valve 95 a is adjusted so that a target value is achieved in the degree of superheat of the refrigerant at the outlet in the third intake return tube 95 side of the subcooling heat exchanger 96. In the present modification, the degree of superheat of the refrigerant at the outlet in the third intake return tube 95 side of the subcooling heat exchanger 96 is obtained by converting the low pressure detected by the intake pressure sensor 60 to a saturation temperature and subtracting this refrigerant saturation temperature value from the refrigerant temperature detected by the subcooling heat exchanger outlet temperature sensor 59. Though not used in the present modification, another possible option is to provide a temperature sensor to the inlet in the third intake return tube 95 side of the subcooling heat exchanger 96, and to obtain the degree of superheat of the refrigerant at the outlet in the third intake return tube 95 side of the subcooling heat exchanger 96 by subtracting the refrigerant temperature detected by this temperature sensor from the refrigerant temperature detected by the subcooling heat exchanger outlet temperature sensor 59. Adjusting the opening degree of the third intake return valve 95 a is not limited to the superheat degree control, and the third intake return valve 95 a may be opened to a predetermined opening degree in accordance with the flow rate of refrigerant circulating within the refrigerant circuit 410, for example.

When the refrigerant circuit 410 is in this state, low-pressure refrigerant (refer to point A in FIGS. 22 through 24) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 22 through 24). The intermediate-pressure refrigerant discharged from the first-stage compression element 2 c is cooled by heat exchange with water or air as a cooling source in the intermediate heat exchanger 7 (refer to point C1 in FIGS. 22 to 24). The refrigerant cooled in the intermediate heat exchanger 7 is further cooled (refer to point G in FIGS. 22 to 24) by being mixed with refrigerant being returned from the first second-stage injection tube 19 to the second-stage compression element 2 d (refer to point K in FIGS. 22 to 24). Next, having been mixed with the refrigerant returning from the first second-stage injection tube 19 (i.e., intermediate pressure injection is carried out by the economizer heat exchanger 20), the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 22 through 24). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 23). The high-pressure refrigerant discharged from the compression mechanism 2 is fed via the switching mechanism 3 to the heat source-side heat exchanger 4 functioning as a refrigerant radiator, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point E in FIGS. 22 to 24). Some of the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator is then branched off to the first second-stage injection tube 19. The refrigerant flowing through the first second-stage injection tube 19 is depressurized to a nearly intermediate pressure in the first second-stage injection valve 19 a and is then fed to the economizer heat exchanger 20 (refer to point 3 in FIGS. 22 to 24). The refrigerant branched off to the first second-stage injection tube 19 then flows into the economizer heat exchanger 20, where it is cooled by heat exchange with the refrigerant flowing through the first second-stage injection tube 19 (refer to point H in FIGS. 20 to 22). The refrigerant flowing through the first second-stage injection tube 19 is heated by heat exchange with the high-pressure refrigerant cooled in the heat source-side heat exchanger 4 as a radiator (refer to point K in FIGS. 22 to 24), and is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The high-pressure refrigerant cooled in the economizer heat exchanger 20 is depressurized to a nearly saturated pressure by the first expansion mechanism 5 a and is temporarily retained in the receiver 18 (refer to point I in FIGS. 22 to 24). Some of the refrigerant retained in the receiver 18 is then branched off to the third intake return tube 95. The refrigerant flowing through the third intake return tube 95 is depressurized to a nearly low pressure in the third intake return valve 95 a and is then fed to the subcooling heat exchanger 96 (refer to point S in FIGS. 20 to 22). The refrigerant branched off to the third intake return tube 95 then flows into the subcooling heat exchanger 96, where it is further cooled by heat exchange with the refrigerant flowing through the third intake return tube 95 (refer to point R in FIGS. 22 to 24). The refrigerant flowing through the third intake return tube 95 is heated by heat exchange with the high-pressure refrigerant cooled in the economizer heat exchanger 20 (refer to point U in FIGS. 22 to 24), and is mixed with the refrigerant flowing through the intake side of the compression mechanism 2 (here, the intake tube 2 a). The refrigerant cooled in the subcooling heat exchanger 96 is then fed to the usage-side expansion mechanisms 5 c and depressurized by the usage-side expansion mechanisms 5 c to become a low-pressure gas-liquid two-phase refrigerant, and is then fed to the usage-side heat exchangers 6 functioning as evaporators of refrigerant (refer to point F in FIGS. 22 to 24). The low-pressure gas-liquid two-phase refrigerant fed to the usage-side heat exchangers 6 that function as evaporators is heated by heat exchange with water or air as a heating source, and the refrigerant is evaporated as a result (refer to point A in FIGS. 22 to 24). The low-pressure refrigerant heated and evaporated in the usage-side heat exchangers 6 that function as evaporators is then drawn back into the compression mechanism 2 via the switching mechanism 3. In this manner the air-cooling operation is performed.

<Air-Warming Operation>

During the air-warming operation, the switching mechanism 3 is brought to the heating operation state shown by the dashed lines in FIG. 22. The opening degrees of the first expansion mechanism 5 a and the usage-side expansion mechanisms 5 c as heat source-side expansion mechanisms are adjusted. Since the switching mechanism 3 is set to the heating operation state, the intermediate heat exchanger on/off valve 12 of the intermediate refrigerant tube 8 is closed and the intermediate heat exchanger bypass on/off valve 11 of the intermediate heat exchanger bypass tube 9 is opened, thereby putting the intermediate heat exchanger 7 into a state of not functioning as a cooler. Furthermore, since the switching mechanism 3 is in the heating operation state, opening the second intake return on/off valve 92 a of the second intake return tube 92 creates a state in which the intermediate heat exchanger 7 and the intake side of the compression mechanism 2 are connected, and opening the intermediate heat exchanger return on/off valve 94 a of the intermediate heat exchanger return tube 94 creates a state in which the portion between the usage-side heat exchangers 6 and the heat source-side heat exchanger 4 is connected with the intermediate heat exchanger 7. When the switching mechanism 3 has been set to the heating operation state, intermediate pressure injection is not performed by the economizer heat exchanger 20, but instead intermediate pressure injection is performed by the receiver 18 for returning the refrigerant from the receiver 18 as a gas-liquid separator to the second-stage compression element 2 d through the second second-stage injection tube 18 c. More specifically, the second second-stage injection on/off valve 18 d is opened, and the first second-stage injection valve 19 a is fully closed. When the switching mechanism 3 has been set to the heating operation state, the third intake return valve 95 a is also fully closed because the subcooling heat exchanger 96 is not used.

When the refrigerant circuit 410 is in this state, low-pressure refrigerant (refer to point A in FIGS. 22, 20, and 21) is drawn into the compression mechanism 2 through the intake tube 2 a, and after the refrigerant is first compressed to an intermediate pressure by the compression element 2 c, the refrigerant is discharged to the intermediate refrigerant tube 8 (refer to point B1 in FIGS. 22, 20, 21). Unlike the air-cooling operation, the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c passes through the intermediate heat exchanger bypass tube 9 (refer to point C1 in FIGS. 22, 20, and 21) without passing through the intermediate heat exchanger 7 (i.e., without being cooled), and the refrigerant is cooled (refer to point G in FIGS. 22, 20, and 21) by being mixed with refrigerant being returned from the receiver 18 via the second second-stage injection tube 18 c to the second-stage compression element 2 d (refer to point M in FIGS. 22, 20, and 21). Next, having been mixed with the refrigerant returning from the second second-stage injection tube 18 c (i.e., intermediate pressure injection is carried out by the receiver 18 which acts as a gas-liquid separator), the intermediate-pressure refrigerant is drawn into and further compressed in the compression element 2 d connected to the second-stage side of the compression element 2 c, and the refrigerant is discharged from the compression mechanism 2 to the discharge tube 2 b (refer to point D in FIGS. 22, 20, and 21). The high-pressure refrigerant discharged from the compression mechanism 2 is compressed by the two-stage compression action of the compression elements 2 c, 2 d to a pressure exceeding a critical pressure (i.e., the critical pressure Pcp at the critical point CP shown in FIG. 20), similar to the air-cooling operation. The high-pressure refrigerant discharged from the compression mechanism 2 is fed via the switching mechanism 3 to the usage-side heat exchangers 6 functioning as refrigerant radiators, and the refrigerant is cooled by heat exchange with water or air as a cooling source (refer to point F in FIGS. 22, 20, and 21). The high-pressure refrigerant cooled in the usage-side heat exchangers 6 as radiators is then depressurized to a nearly intermediate pressure by the usage-side expansion mechanisms 5 c, and is then temporarily retained in the receiver 18 and subjected to gas-liquid separation (refer to points I, L, and M in FIGS. 22, 20, and 21). The gas refrigerant after having undergone gas-liquid separation in the receiver 18 is then removed out of the top part of the receiver 18 by the second second-stage injection tube 18 c, and is mixed with the intermediate-pressure refrigerant discharged from the first-stage compression element 2 c as described above. The liquid refrigerant retained in the receiver 18 is depressurized by the first expansion mechanism 5 a to become a low-pressure gas-liquid two-phase refrigerant, which is fed to the heat source-side heat exchanger 4 functioning as an evaporator of refrigerant, and is also fed through the intermediate heat exchanger return tube 94 to the intermediate heat exchanger 7 functioning as an evaporator of refrigerant (refer to point E in FIGS. 22, 20, and 21). The low-pressure gas-liquid two-phase refrigerant fed to the heat source-side heat exchanger 4 is heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point A in FIGS. 22, 20, and 21). The low-pressure gas-liquid two-phase refrigerant fed to the intermediate heat exchanger 7 is also heated by heat exchange with water or air as a heating source, and the refrigerant evaporates as a result (refer to point V in FIGS. 22, 20, and 21). The low-pressure refrigerant heated and evaporated in the heat source-side heat exchanger 4 is then drawn back into the compression mechanism 2 via the switching mechanism 3. The low-pressure refrigerant heated and evaporated in the intermediate heat exchanger 7 is then drawn back into the compression mechanism 2 via the second intake return tube 92. In this manner the air-warming operation is performed.

In the configuration of the present modification, the same operational effects as those of Modification 5 described above are achieved, and the risk of an imbalanced flow of refrigerant during distribution to the usage-side expansion mechanisms 5 c can be reduced because the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c during the air-cooling operation (refer to point I in FIGS. 22 to 24) can be cooled to a subcooled state by the subcooling heat exchanger 96 (refer to points I and R in FIGS. 23 and 24).

In the present modification, the switching between the air-cooling operation and air-cooling start control, i.e., the switching between the refrigerant non-return state and the refrigerant return state is performed by the on/off states of the on/off valves 11, 12, 92 a, but an intermediate heat exchanger switching valve 93 capable of switching between the refrigerant non-return state and the refrigerant return state may be provided instead of the on/off valves 11, 12, 92 a, as in Modification 1 described above.

Furthermore, particularly advantageous effects can be obtained when using the configuration of the heat source unit 1 a such as the one in Modification 2.

(8) Modification 6

In the above-described embodiment and the modifications thereof, a two-stage compression-type compression mechanism 2 is configured such that the refrigerant discharged from the first-stage compression element of two compression elements 2 c, 2 d is sequentially compressed in the second-stage compression element by one compressor 21 having a single-axis two-stage compression structure, but other options include using a compression mechanism having more stages than a two-stage compression system, such as a three-stage compression system or the like; or configuring a multistage compression mechanism connecting in series a plurality of compressors incorporated with a single compression element and/or compressors incorporated with a plurality of compression elements. In cases in which the capacity of the compression mechanism must be increased, such as cases in which numerous usage-side heat exchangers 6 are connected, for example, a parallel multistage compression-type compression mechanism may be used in which two or more multistage compression-type compression mechanisms are connected in parallel.

For example, the refrigerant circuit 410 in Modification 5 described above (see FIG. 22) may be replaced by a refrigerant circuit 510 that uses a compression mechanism 102 in which two-stage compression-type compression mechanisms 103, 104 are connected in parallel instead of the two-stage compression-type compression mechanism 2, as shown in FIG. 25.

In the present modification, the first compression mechanism 103 is configured using a compressor 29 for subjecting the refrigerant to two-stage compression through two compression elements 103 c, 103 d, and is connected to a first intake branch tube 103 a which branches off from an intake header tube 102 a of the compression mechanism 102, and also to a first discharge branch tube 103 b whose flow merges with a discharge header tube 102 b of the compression mechanism 102. In the present modification, the second compression mechanism 104 is configured using a compressor 30 for subjecting the refrigerant to two-stage compression through two compression elements 104 c, 104 d, and is connected to a second intake branch tube 104 a which branches off from the intake header tube 102 a of the compression mechanism 102, and also to a second discharge branch tube 104 b whose flow merges with the discharge header tube 102 b of the compression mechanism 102. Since the compressors 29, 30 have the same configuration as the compressor 21 in the embodiment and modifications thereof described above, symbols indicating components other than the compression elements 103 c, 103 d, 104 c, 104 d are replaced with symbols beginning with 29 or 30, and these components are not described here. The compressor 29 is configured so that refrigerant is drawn from the first intake branch tube 103 a, the refrigerant thus drawn in is compressed by the compression element 103 c and then discharged to a first inlet-side intermediate branch tube 81 that constitutes the intermediate refrigerant tube 8, the refrigerant discharged to the first inlet-side intermediate branch tube 81 is caused to be drawn into the compression element 103 d by way of an intermediate header tube 82 and a first outlet-side intermediate branch tube 83 constituting the intermediate refrigerant tube 8, and the refrigerant is further compressed and then discharged to the first discharge branch tube 103 b. The compressor 30 is configured so that refrigerant is drawn in through the second intake branch tube 104 a, the drawn-in refrigerant is compressed by the compression element 104 c and then discharged to a second inlet-side intermediate branch tube 84 constituting the intermediate refrigerant tube 8, the refrigerant discharged to the second inlet-side intermediate branch tube 84 is drawn into the compression element 104 d via the intermediate header tube 82 and a second outlet-side intermediate branch tube 85 constituting the intermediate refrigerant tube 8, and the refrigerant is further compressed and then discharged to the second discharge branch tube 104 b. In the present modification, the intermediate refrigerant tube 8 is a refrigerant tube for drawing in refrigerant discharged from the compression elements 103 c, 104 c connected to the first-stage sides of the compression elements 103 d, 104 d into the compression elements 103 d, 104 d connected to the second-stage sides of the compression elements 103 c, 104 c, and the intermediate refrigerant tube 8 primarily comprises the first inlet-side intermediate branch tube 81 connected to the discharge side of the first-stage compression element 103 c of the first compression mechanism 103, the second inlet-side intermediate branch tube 84 connected to the discharge side of the first-stage compression element 104 c of the second compression mechanism 104, the intermediate header tube 82 whose flow merges with both inlet-side intermediate branch tubes 81, 84, the first outlet-side intermediate branch tube 83 branching off from the intermediate header tube 82 and connected to the intake side of the second-stage compression element 103 d of the first compression mechanism 103, and the second outlet-side intermediate branch tube 85 branching off from the intermediate header tube 82 and connected to the intake side of the second-stage compression element 104 d of the second compression mechanism 104. The discharge header tube 102 b is a refrigerant tube for feeding refrigerant discharged from the compression mechanism 102 to the switching mechanism 3. A first oil separation mechanism 141 and a first non-return mechanism 142 are provided to the first discharge branch tube 103 b connected to the discharge header tube 102 b. A second oil separation mechanism 143 and a second non-return mechanism 144 are provided to the second discharge branch tube 104 b connected to the discharge header tube 102 b. The first oil separation mechanism 141 is a mechanism whereby refrigeration oil that accompanies the refrigerant discharged from the first compression mechanism 103 is separated from the refrigerant and returned to the intake side of the compression mechanism 102. The first oil separation mechanism 141 mainly has a first oil separator 141 a for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the first compression mechanism 103, and a first oil return tube 141 b that is connected to the first oil separator 141 a and that is used for returning the refrigeration oil separated from the refrigerant to the intake side of the compression mechanism 102. The second oil separation mechanism 143 is a mechanism whereby refrigeration oil that accompanies the refrigerant discharged from the second compression mechanism 104 is separated from the refrigerant and returned to the intake side of the compression mechanism 102. The second oil separation mechanism 143 mainly has a second oil separator 143 a for separating from the refrigerant the refrigeration oil that accompanies the refrigerant discharged from the second compression mechanism 104, and a second oil return tube 143 b that is connected to the second oil separator 143 a and that is used for returning the refrigeration oil separated from the refrigerant to the intake side of the compression mechanism 102. In the present modification, the first oil return tube 141 b is connected to the second intake branch tube 104 a, and the second oil return tube 143 c is connected to the first intake branch tube 103 a. Accordingly, a greater amount of refrigeration oil returns to the compression mechanism 103, 104 that has the lesser amount of refrigeration oil even when there is an imbalance between the amount of refrigeration oil that accompanies the refrigerant discharged from the first compression mechanism 103 and the amount of refrigeration oil that accompanies the refrigerant discharged from the second compression mechanism 104, which is due to the imbalance in the amount of refrigeration oil retained in the first compression mechanism 103 and the amount of refrigeration oil retained in the second compression mechanism 104. The imbalance between the amount of refrigeration oil retained in the first compression mechanism 103 and the amount of refrigeration oil retained in the second compression mechanism 104 is therefore resolved. In the present modification, the first intake branch tube 103 a is configured so that the portion leading from the flow juncture with the second oil return tube 143 b to the flow juncture with the intake header tube 102 a slopes downward toward the flow juncture with the intake header tube 102 a, while the second intake branch tube 104 a is configured so that the portion leading from the flow juncture with the first oil return tube 141 b to the flow juncture with the intake header tube 102 a slopes downward toward the flow juncture with the intake header tube 102 a. Therefore, even if either one of the compression mechanisms 103, 104 is stopped, refrigeration oil being returned from the oil return tube corresponding to the operating compression mechanism to the intake branch tube corresponding to the stopped compression mechanism is returned to the intake header tube 102 a, and there will be little likelihood of a shortage of oil supplied to the operating compression mechanism. The oil return tubes 141 b, 143 b are provided with pressure-reducing mechanisms 141 c, 143 c for depressurizing the refrigeration oil that flows through the oil return tubes 141 b, 143 b. The non-return mechanisms 142, 144 are mechanisms for allowing refrigerant to flow from the discharge side of the compression mechanisms 103, 104 to the switching mechanism 3, and for blocking the flow of refrigerant from the switching mechanism 3 to the discharge side of the compression mechanisms 103, 104.

Thus, in the present modification, the compression mechanism 102 is configured by connecting two compression mechanisms in parallel; namely, the first compression mechanism 103 having two compression elements 103 c, 103 d and configured so that refrigerant discharged from the first-stage compression element of these compression elements 103 c, 103 d is sequentially compressed by the second-stage compression element, and the second compression mechanism 104 having two compression elements 104 c, 104 d and configured so that refrigerant discharged from the first-stage compression element of these compression elements 104 c, 104 d is sequentially compressed by the second-stage compression element.

In the present modification, the intermediate heat exchanger 7 is provided to the intermediate header tube 82 constituting the intermediate refrigerant tube 8, and the intermediate heat exchanger 7 is a heat exchanger for cooling the mixed flow of the refrigerant discharged from the first-stage compression element 103 c of the first compression mechanism 103 and the refrigerant discharged from the first-stage compression element 104 c of the second compression mechanism 104. Specifically, the intermediate heat exchanger 7 functions as a shared cooler for two compression mechanisms 103, 104. Accordingly, the circuit configuration is simplified around the compression mechanism 102 when the intermediate heat exchanger 7 is provided to the parallel-multistage-compression-type compression mechanism 102 in which a plurality of multistage-compression-type compression mechanisms 103, 104 are connected in parallel.

The first inlet-side intermediate branch tube 81 constituting the intermediate refrigerant tube 8 is provided with a non-return mechanism 81 a for allowing the flow of refrigerant from the discharge side of the first-stage compression element 103 c of the first compression mechanism 103 toward the intermediate header tube 82 and for blocking the flow of refrigerant from the intermediate header tube 82 toward the discharge side of the first-stage compression element 103 c, while the second inlet-side intermediate branch tube 84 constituting the intermediate refrigerant tube 8 is provided with a non-return mechanism 84 a for allowing the flow of refrigerant from the discharge side of the first-stage compression element 104 c of the second compression mechanism 104 toward the intermediate header tube 82 and for blocking the flow of refrigerant from the intermediate header tube 82 toward the discharge side of the first-stage compression element 104 c. In the present modification, non-return valves are used as the non-return mechanisms 81 a, 84 a. Therefore, even if either one of the compression mechanisms 103, 104 has stopped, there are no instances in which refrigerant discharged from the first-stage compression element of the operating compression mechanism passes through the intermediate refrigerant tube 8 and travels to the discharge side of the first-stage compression element of the stopped compression mechanism. Accordingly, there are no instances in which refrigerant discharged from the first-stage compression element of the operating compression mechanism passes through the interior of the first-stage compression element of the stopped compression mechanism and exits out through the intake side of the compression mechanism 102, which would cause the refrigeration oil of the stopped compression mechanism to flow out, and it is thus unlikely that there will be insufficient refrigeration oil for starting up the stopped compression mechanism. In the case that the compression mechanisms 103, 104 are operated in order of priority (for example, in the case of a compression mechanism in which priority is given to operating the first compression mechanism 103), the stopped compression mechanism described above will always be the second compression mechanism 104, and therefore in this case only the non-return mechanism 84 a corresponding to the second compression mechanism 104 need be provided.

In cases of a compression mechanism which prioritizes operating the first compression mechanism 103 as described above, since a shared intermediate refrigerant tube 8 is provided for both compression mechanisms 103, 104, the refrigerant discharged from the first-stage compression element 103 c corresponding to the operating first compression mechanism 103 passes through the second outlet-side intermediate branch tube 85 of the intermediate refrigerant tube 8 and travels to the intake side of the second-stage compression element 104 d of the stopped second compression mechanism 104, whereby there is a danger that refrigerant discharged from the first-stage compression element 103 c of the operating first compression mechanism 103 will pass through the interior of the second-stage compression element 104 d of the stopped second compression mechanism 104 and exit out through the discharge side of the compression mechanism 102, causing the refrigeration oil of the stopped second compression mechanism 104 to flow out, resulting in insufficient refrigeration oil for starting up the stopped second compression mechanism 104. In view of this, an on/off valve 85 a is provided to the second outlet-side intermediate branch tube 85 in the present modification, and when the second compression mechanism 104 has stopped, the flow of refrigerant through the second outlet-side intermediate branch tube 85 is blocked by the on/off valve 85 a. The refrigerant discharged from the first-stage compression element 103 c of the operating first compression mechanism 103 thereby no longer passes through the second outlet-side intermediate branch tube 85 of the intermediate refrigerant tube 8 and travels to the intake side of the second-stage compression element 104 d of the stopped second compression mechanism 104; therefore, there are no longer any instances in which the refrigerant discharged from the first-stage compression element 103 c of the operating first compression mechanism 103 passes through the interior of the second-stage compression element 104 d of the stopped second compression mechanism 104 and exits out through the discharge side of the compression mechanism 102 which causes the refrigeration oil of the stopped second compression mechanism 104 to flow out, and it is thereby even more unlikely that there will be insufficient refrigeration oil for starting up the stopped second compression mechanism 104. An electromagnetic valve is used as the on/off valve 85 a in the present modification.

In the case of a compression mechanism which prioritizes operating the first compression mechanism 103, the second compression mechanism 104 is started up in continuation from the starting up of the first compression mechanism 103, but at this time, since a shared intermediate refrigerant tube 8 is provided for both compression mechanisms 103, 104, the starting up takes place from a state in which the pressure in the discharge side of the first-stage compression element 103 c of the second compression mechanism 104 and the pressure in the intake side of the second-stage compression element 103 d are greater than the pressure in the intake side of the first-stage compression element 103 c and the pressure in the discharge side of the second-stage compression element 103 d, and it is difficult to start up the second compression mechanism 104 in a stable manner. In view of this, in the present modification, there is provided a startup bypass tube 86 for connecting the discharge side of the first-stage compression element 104 c of the second compression mechanism 104 and the intake side of the second-stage compression element 104 d, and an on/off valve 86 a is provided to this startup bypass tube 86. In cases in which the second compression mechanism 104 has stopped, the flow of refrigerant through the startup bypass tube 86 is blocked by the on/off valve 86 a and the flow of refrigerant through the second outlet-side intermediate branch tube 85 is blocked by the on/off valve 85 a. When the second compression mechanism 104 is started up, a state in which refrigerant is allowed to flow through the startup bypass tube 86 can be restored via the on/off valve 86 a, whereby the refrigerant discharged from the first-stage compression element 104 c of the second compression mechanism 104 is drawn into the second-stage compression element 104 d via the startup bypass tube 86 without being mixed with the refrigerant discharged from the first-stage compression element 104 c of the first compression mechanism 103, a state of allowing refrigerant to flow through the second outlet-side intermediate branch tube 85 can be restored via the on/off valve 85 a at point in time when the operating state of the compression mechanism 102 has been stabilized (e.g., a point in time when the intake pressure, discharge pressure, and intermediate pressure of the compression mechanism 102 have been stabilized), the flow of refrigerant through the startup bypass tube 86 can be blocked by the on/off valve 86 a, and operation can transition to the normal air-cooling operation. In the present modification, one end of the startup bypass tube 86 is connected between the on/off valve 85 a of the second outlet-side intermediate branch tube 85 and the intake side of the second-stage compression element 104 d of the second compression mechanism 104, while the other end is connected between the discharge side of the first-stage compression element 104 c of the second compression mechanism 104 and the non-return mechanism 84 a of the second inlet-side intermediate branch tube 84, and when the second compression mechanism 104 is started up, the startup bypass tube 86 can be kept in a state of being substantially unaffected by the intermediate pressure portion of the first compression mechanism 103. An electromagnetic valve is used as the on/off valve 86 a in the present modification.

The action of the air-conditioning apparatus 1 of the present modification during the air-cooling operation, the air-warming operation, and the like are essentially the same as the action in the above-described Modification 5 (FIGS. 22 through 24, 20, and 21 and the relevant descriptions), except that the points modified by the circuit configuration surrounding the compression mechanism 102 are somewhat more complex due to the compression mechanism 102 being provided instead of the compression mechanism 2, for which reason the action is not described herein.

The same operational effects as those of Modification 5 described above can also be achieved with the configuration of the present modification.

In the present modification, the switching between the air-cooling operation and air-cooling start control, i.e., the switching between the refrigerant non-return state and the refrigerant return state is performed by the on/off states of the on/off valves 11, 12, 92 a, but an intermediate heat exchanger switching valve 93 capable of switching between the refrigerant non-return state and the refrigerant return state may be provided instead of the on/off valves 11, 12, 92 a, as in Modification 1 described above.

Furthermore, particularly advantageous effects can be obtained when using the configuration of the heat source unit 1 a such as the one in Modification 2.

(9) Modification 7

In the above-described embodiment and the modifications thereof, either a two-stage compression-type compression mechanism 2 is configured such that the refrigerant discharged from the first-stage compression element is sequentially compressed in the second-stage compression element by one compressor 21 having a single-axis two-stage compression structure, or a two-stage compression-type compression mechanism 102 is configured such that two single-axis two-stage compression-type compressors 29, 30 are connected in parallel, whereby the refrigerant discharged from the first-stage compression element is sequentially compressed by the second-stage compression element; but another option is to configure a two-stage compression-type compression mechanism such that compressors 22, 23 having single-stage compression structures are connected in series, whereby the refrigerant discharged from the first-stage compression element is sequentially compressed by the second-stage compression element.

For example, the refrigerant circuit 110 in Modification 1 described above (see FIG. 10) may be replaced by a refrigerant circuit 610 that uses a compression mechanism 202 in which compressors 22, 23 having single-stage compression structures are connected in series instead of the compression mechanism 2 composed of a compressor 21 having a single-axis two-stage compression structure, as shown in FIG. 26.

In the present modification, the compression mechanism 202 is configured from a compressor 22 in which refrigerant is compressed by a compression element 202 c as a first-stage compression element, and a compressor 23 in which refrigerant is compressed by a compression element 202 d as a second-stage compression element. The compressor 22 has a hermetic structure in which a casing 22 a houses a compressor drive motor 22 b, a drive shaft 22 c, and a compression element 202 c. The compressor drive motor 22 b is linked to the drive shaft 22 c. The compressor 23 has a hermetic structure in which a casing 23 a houses a compressor drive motor 23 b, a drive shaft 23 c, and a compression element 202 d. The compressor drive motor 23 b is linked to the drive shaft 23 c. In the present modification, the compression elements 202 c, 202 d are rotary elements, scroll elements, or another type of positive displacement compression element. The compression mechanism 202 is configured so as to draw in refrigerant through an intake tube 2 a, to discharge this refrigerant to an intermediate refrigerant tube 8 after the refrigerant has been compressed by the compression element 202 c of the compressor 22, to admit the refrigerant discharged to the intermediate refrigerant tube 8 into the compression element 202 d of the compressor 23, and to discharge the refrigerant to a discharge tube 2 b after the refrigerant has been further compressed.

The action of the air-conditioning apparatus 1 of the present modification during the air-cooling operation, the air-warming operation, and the like are essentially the same as the action in the above-described Modification 1 (FIGS. 10 and 1 through 9 and the relevant descriptions), except for the compression mechanism 2 being replaced by the compression mechanism 202, for which reason the action is not described herein.

The same operational effects as those of Modification 1 and the like described above can also be obtained with the configuration of the present modification.

(10) Modification 8

In the embodiment described above and the modifications thereof, the intermediate heat exchanger return tube 94 is provided with the intermediate heat exchanger return on/off valve 94 a composed of an electromagnetic valve, and control is performed for closing the valve when the switching mechanism 3 is in the cooling operation state and opening the valve when the switching mechanism 3 is in the heating operation state, but instead of this intermediate heat exchanger return on/off valve 94 a, another option is to provide a flow rate control valve so as to enable control of the quantity of refrigerant flowing through the intermediate heat exchanger 7 functioning as an evaporator of refrigerant during the air-warming operation.

For example, the refrigerant circuit 610 in Modification 7 described above (see FIG. 26) may be replaced with a refrigerant circuit 710 provided with an intermediate heat exchanger return valve 94 b as a flow rate control valve instead of the intermediate heat exchanger return on/off valve 94 a, as shown in FIG. 27. In the present modification, an electrically driven expansion valve whose opening degree can be adjusted is used as the intermediate heat exchanger return valve 94 b. When the intermediate heat exchanger return valve 94 b is provided, the first expansion mechanism 5 a provided to the receiver inlet tube 18 a is provided to a refrigerant tube 18 h connecting the heat source-side heat exchanger 4 and the bridge circuit 17 together (more specifically, to the portion of the refrigerant tube 18 h between the branching position of the intermediate heat exchanger return tube 94 and the heat source-side heat exchanger 4), thereby ensuring a pressure difference in the area before the intermediate heat exchanger return valve 94 b and the area after the intermediate heat exchanger return valve 94 b. The second expansion mechanism 5 b provided to the receiver outlet tube 18 b is also provided to a refrigerant tube 18 i connecting the bridge circuit 17 and the usage-side heat exchanger 6 together, whereby the pressure of the refrigerant in the receiver 18 is brought to an intermediate pressure in the refrigeration cycle.

The configuration of the present modification is different from that of Modification 7 described above in that refrigerant flows in the refrigerant circuit 710 sequentially through the first expansion mechanism 5 a, the receiver 18, and the second expansion mechanism 5 b via the bridge circuit 17 during the air-cooling operation and refrigerant flows in the refrigerant circuit 710 sequentially through the second expansion mechanism 5 b, the receiver 18, and the first expansion mechanism 5 a via the bridge circuit 17 during the air-warming operation (in Modification 7, refrigerant flows in the refrigerant circuit 610 sequentially through the first expansion mechanism 5 a, the receiver, and the second expansion mechanism 5 b during both the air-cooling operation and the air-warming operation), but otherwise the same operational effects as those of Modification 7 described above can be obtained. Moreover, in the configuration of the present modification, since the intermediate heat exchanger return valve 94 b as a flow rate control valve is provided to the intermediate heat exchanger return tube 94, not only can the flow of refrigerant into the intermediate heat exchanger return tube 94 be prevented during the air-cooling operation, but it is also possible to reliably distribute the flow rate of refrigerant flowing through the heat source-side heat exchanger 4 and the flow rate of refrigerant flowing through the intermediate heat exchanger 7 during the heating operation.

(11) Modification 9

In the configurations of the above-described embodiment and the modifications thereof, an expansion device for isentropically expanding the refrigerant flowing between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6 may be provided between the heat source-side heat exchanger 4 and the usage-side heat exchanger 6.

For example, the refrigerant circuit 710 in Modification 8 described above (see FIG. 27) may be replaced with a refrigerant circuit 810 in which an expansion device 97 for isentropically expanding the refrigerant is provided to the receiver inlet tube 18 a, as shown in FIG. 28. Specifically, in the present modification, the expansion device 97 is connected via the bridge circuit 17 as a rectifier circuit for rectifying the refrigerant flow so that the refrigerant flows in from the inlet of the expansion device 97, both in cases in which the refrigerant flows from the heat source-side heat exchanger 4 to the usage-side heat exchanger 6 and cases in which the refrigerant flows from the usage-side heat exchanger 6 to the heat source-side heat exchanger 4. In the present modification, a centrifugal or positive displacement expansion device is used as the expansion device 97. In the present modification, the bridge circuit 17 is used as a rectifier circuit, but the configuration may also be designed so that the same function is fulfilled by a four-way switching valve or by combining a plurality of electromagnetic valves.

The same operational effects as those of Modification 8 and the like described above can also be obtained with the configuration of the present modification. Moreover, in the configuration of the present modification, during the air-cooling operation, refrigerant flows in the refrigerant circuit 810 sequentially through the first expansion mechanism 5 a, the expansion device 97, the receiver 18, and the second expansion mechanism 5 b via the bridge circuit 17 as a rectifier circuit, and during the air-warming operation, refrigerant flows in the refrigerant circuit 810 sequentially through the second expansion mechanism 5 b, the receiver 18, and the first expansion mechanism 5 a via the bridge circuit 17 as a rectifier circuit, whereby the refrigerant is isentropically depressurized by the expansion device 97 during the process in which the refrigerant is depressurized from a high pressure to a low pressure in the refrigeration cycle during both the air-cooling operation and the air-warming operation (in other words, during the air-cooling operation, using FIGS. 3 and 4 as examples, the refrigerant is depressurized while point F moves to an area of lower enthalpy and lower entropy; and during the air-warming operation, using FIGS. 6 and 7 as examples, the refrigerant is depressurized while point E moves to an area of lower enthalpy and lower entropy). It is thereby possible to improve the coefficient of performance and to recover energy, and operation efficiency during both the air-cooling operation and the air-warming operation can therefore be further improved. In the present modification, the depressurizing range in the expansion device 97 may be increased to maximize the improvement of operating efficiency, either by performing control for increasing the opening degree of the second expansion mechanism 5 b downstream of the expansion device 97 and/or control for opening the first intake return on/off valve 18 g during the air-cooling operation, or by performing control for increasing the opening degree of the first expansion mechanism 5 a downstream of the expansion device 97 and/or control for opening the first intake return on/off valve 18 g during the air-cooling operation, for example.

(12) Modification 10

In the configuration of Modification 9 described above, the receiver 18 positioned in the outlet of the expansion device 97 may be made to function as a gas-liquid separator, a second-stage injection tube may be connected for returning the gas refrigerant separated from the liquid in the receiver 18 to the second-stage compression element 2 d, and intermediate pressure injection may be performed by the receiver 18 as a gas-liquid separator during both the air-cooling operation and the air-warming operation.

For example, the refrigerant circuit 810 (see FIG. 28) in Modification 9 described above may be replaced by a refrigerant circuit 910 in which the second second-stage injection tube 18 c is connected to the receiver 18, and intermediate pressure injection can be performed by the receiver 18 as a gas-liquid separator, as shown in FIG. 29.

The second second-stage injection tube 18 c is a refrigerant tube capable of performing intermediate pressure injection for removing refrigerant out of the receiver 18 and returning the refrigerant to the second-stage compression element 202 d of the compression mechanism 202, and in the present modification, the second second-stage injection tube 18 c is provided so as to connect the top part of the receiver 18 with the intermediate refrigerant tube 8 (i.e., with the intake side of the second-stage compression element 202 d of the compression mechanism 202). The second second-stage injection on/off valve 18 d and the second second-stage injection non-return mechanism 18 e are provided to the second second-stage injection tube 18 c. The second second-stage injection on/off valve 18 d is a valve capable of opening and closing, and is an electromagnetic valve in the present modification. The second second-stage injection non-return mechanism 18 e is a mechanism for allowing the flow of refrigerant from the receiver 18 to the second-stage compression element 202 d and for blocking the flow of refrigerant from the second-stage compression element 202 d to the receiver 18, and a non-return valve is used in the present modification. The second second-stage injection tube 18 c and the first intake return tube 18 f are integrated in the portion near the receiver 18.

The same operational effects as those of Modification 9 described above can also be obtained with the configuration of the present modification. Moreover, in the configuration of the present modification, operation efficiency can be further improved because it is also possible, during both the air-cooling operation and the air-warming operation, to cause the receiver 18 connected to the outlet of the expansion device 97 to function as a gas-liquid separator, to perform intermediate pressure injection for returning the gas refrigerant separated from the liquid in the receiver 18 to the second-stage compression element 202 d through the second second-stage injection tube 18 c (i.e., using FIGS. 20 and 21 as examples, to perform a process for returning from point I to point G by way of point M), and thereby to reduce the temperature of the intermediate-pressure refrigerant in the refrigeration cycle drawn into the second-stage compression element 202 d.

(13) Modification 11

In Modifications 7 through 10 described above, the configuration may be designed having a plurality of usage-side heat exchangers 6 connected in parallel to each other, the objective being to perform air cooling or air warming according to the air-conditioning load of a plurality of air-conditioned spaces, for example.

For example, the refrigerant circuits 810 and 910 in Modifications 9 and 10 described above (see FIGS. 28 and 29) may be replaced by refrigerant circuits 1010 and 1110 having a plurality (two in this case) of usage-side heat exchangers 6 connected to each other in parallel, as shown in FIGS. 30 and 31. When a plurality of usage-side heat exchangers 6 are provided, in order to control the flow rate of the refrigerant flowing through the usage-side heat exchangers 6 and ensure that the refrigeration load required by the usage-side heat exchangers 6 can be obtained, usage-side expansion mechanisms 5 c are provided instead of the second expansion mechanism 5 b between the receiver 18 and the usage-side heat exchangers 6, so as to correspond to the usage-side heat exchangers 6 (i.e., to portions in the refrigerant tube 18 i branching off toward the usage-side heat exchangers 6).

The same operational effects as those of Modifications 9 and 10 and the like described above can also be obtained with the configuration of the present modification.

(14) Modification 12

In Modifications 7 through 11 described above, a subcooler may be provided, the objective being to cool the refrigerant fed to the usage-side heat exchanger 6 and the heat source-side heat exchanger 4 so that the refrigerant reaches a subcooled state.

For example, the refrigerant circuit 1010 in Modification 11 described above (see FIG. 30) may be replaced by a refrigerant circuit 1210, as shown in FIG. 32, in which a subcooling heat exchanger 96 is provided to the receiver outlet tube 18 b and a third intake return tube 95 is provided to the portion extending through the receiver 18 from the receiver inlet tube 18 a to the receiver outlet tube 18 b (i.e., is provided to the receiver 18).

The subcooling heat exchanger 96 is a heat exchanger for cooling refrigerant fed from the receiver 18 through the plurality (two in this case) of usage-side expansion mechanisms 5 c to the usage-side heat exchangers 6 during the air-cooling operation, and also for cooling refrigerant fed from the receiver 18 through the first expansion mechanism 5 a and the intermediate heat exchanger return valve 94 b to the heat source-side heat exchanger 4 and the intermediate heat exchanger 7 during the air-warming operation. More specifically, the subcooling heat exchanger 96 is a heat exchanger for performing heat exchange with the refrigerant flowing through the third intake return tube 95 which returns from the receiver 18 to the intake side of the compression mechanism 2 (i.e., to the intake tube 2 a). The third intake return tube 95 is provided with a third intake return valve 95 a whose opening degree can be controlled, and during the air-cooling operation in the subcooling heat exchanger 96, heat exchange is performed between the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c and the refrigerant flowing through the third intake return tube 95 after being depressurized to a nearly low pressure in the third intake return valve 95 a, and heat exchange is also performed between the refrigerant fed from the receiver 18 to the first expansion mechanism 5 a and the intermediate heat exchanger return valve 94 b and the refrigerant flowing through the third intake return tube 95 after being depressurized to a nearly low pressure in the third intake return valve 95 a. The third intake return valve 95 a is an electrically driven expansion valve in the present modification. The third intake return tube 95 and the first intake return tube 18 f are integrated in the portion near the receiver 18.

The same operational effects as those of Modification 11 and the like described above can also be obtained with the configuration of the present modification. Moreover, in the configuration of the present modification, the refrigerant fed from the receiver 18 to the usage-side expansion mechanisms 5 c can be brought to a subcooled state during the air-cooling operation, and the refrigerant fed from the receiver 18 to the first expansion mechanism 5 a and the intermediate heat exchanger return valve 94 b can be brought to a subcooled state during the air-warming operation (in other words, using FIGS. 23 and 24 as examples, the process from point I to point R is performed). Therefore, it is thereby possible to reduce the risk of an imbalanced flow of refrigerant being distributed to the usage-side expansion mechanisms 5 c during the air-cooling operation, and also to reduce the risk of an imbalanced flow of refrigerant being distributed to the first expansion mechanism 5 a and the intermediate heat exchanger return valve 94 b during the air-warming operation.

(15) Modification 13

In the above-described embodiment and the modifications thereof, two-stage compression-type compression mechanisms 2, 102, 202 are used, but three-stage compression systems or compression mechanisms having even more stages may also be used.

For example, in the refrigerant circuit 1010 in Modification 11 described above (see FIG. 30), a three-stage compression-type compression mechanism 302 may be used in which single-stage-compression compressors 25, 26, 27 identical to the compressors 22, 23 constituting the compression mechanism 202 are connected in series; the intermediate refrigerant tube 8 for connecting the discharge of the first compressor 25 and the intake of the second compressor 26 may be provided with the same intermediate heat exchanger 7, intermediate heat exchanger bypass tube 9, second intake return tube 92, intermediate heat exchanger switching valve 93, and intermediate heat exchanger return tube 94 as those of the above-described embodiment and modifications thereof; and an intermediate refrigerant tube 308 for connecting the intake of the second compressor 26 with the third compressor 27 may be provided with an intermediate heat exchanger 307, an intermediate heat exchanger bypass tube 309, a second intake return tube 392, an intermediate heat exchanger switching valve 393, and an intermediate heat exchanger return tube 394 identical to the intermediate heat exchanger 7, the intermediate heat exchanger bypass tube 9, the second intake return tube 92, the intermediate heat exchanger switching valve 93, and the intermediate heat exchanger return tube 94, as shown in FIG. 33.

The configuration of the present modification differs from that of the above-described Modification 11, for example, in that since the three-stage compression-type compression mechanism 302 is used, the intermediate heat exchangers 7, 307 can be made to function as coolers of the intermediate-pressure refrigerant in the refrigeration cycle (the refrigerant fed to the second-stage compression element 302 d after being discharged from the first-stage compression element 302 c, and the refrigerant fed to the second-stage compression element 302 e after being discharged from the first-stage compression element 303 c) by switching the intermediate heat exchanger switching valves 93, 393 to the refrigerant non-return state during the air-cooling operation, and the intermediate heat exchangers 7, 307 can be made to function as evaporators of the low-pressure refrigerant in the refrigeration cycle (the refrigerant whose heat is radiated in the usage-side heat exchangers 6) by switching the intermediate heat exchanger switching valves 93, 393 to the refrigerant return state during the air-warming operation. However, aside from this difference, it is possible to obtain the same operational effects as those of the above-described Modification 11, for example.

(16) Other Embodiments

Embodiments of the present invention and modifications thereof are described above with reference to the drawings, but the specific configuration is not limited to these embodiments or their modifications, and can be changed within a range that does not deviate from the scope of the invention.

For example, in the above-described embodiment and modifications thereof, the present invention may be applied to a “chiller-type” air-conditioning apparatus in which water or brine is used as a heating source or cooling source for conducting heat exchange with the refrigerant flowing through the usage-side heat exchanger 6, and a secondary heat exchanger is provided for conducting heat exchange between indoor air and the water or brine that has undergone heat exchange in the usage-side heat exchanger 6.

The present invention can also be applied to other types of refrigeration apparatuses besides the above-described chiller-type air-conditioning apparatus, as long as the apparatus performs a multistage compression refrigeration cycle using a refrigerant that operates in a supercritical range as its refrigerant.

The refrigerant that operates in a supercritical range is not limited to carbon dioxide; ethylene, ethane, nitric oxide, and other gases may also be used.

INDUSTRIAL APPLICABILITY

If the present invention is used, high operation efficiency is obtained in a refrigeration apparatus which has a refrigerant circuit configured to be capable of switching between a cooling operation and a heating operation and which performs a multistage compression-type refrigeration cycle. 

1. A refrigeration apparatus, comprising: a compression mechanism having a plurality of compression elements arranged and configured so that refrigerant discharged from a first-stage compression element of the plurality of compression elements is sequentially compressed by a second-stage compression element of the plurality of compression elements; a heat source-side heat exchanger arranged and configured to function as a radiator or evaporator of refrigerant; a usage-side heat exchanger arranged and configured to function as an evaporator or radiator of refrigerant; a switching mechanism arranged and configured to switch between a cooling operation state in which refrigerant is sequentially circulated through the compression mechanism, the heat source-side heat exchanger functioning as a refrigerant radiator, and the usage-side heat exchanger functioning as an evaporator of refrigerant; and a heating operation state in which refrigerant is sequentially circulated through the compression mechanism, the usage-side heat exchanger functioning as a refrigerant radiator, and the heat source-side heat exchanger functioning as an evaporator of refrigerant; and an intermediate heat exchanger arranged and configured to cool refrigerant discharged from the first-stage compression element and drawn into the second-stage compression element when the switching mechanism has been set to the cooling operation state, and evaporate refrigerant whose heat is radiated in the usage-side heat exchanger when the switching mechanism has been set to the heating operation state.
 2. The refrigeration apparatus according to claim 1, further comprising an intake return tube arranged and configured to connect one end of the intermediate heat exchanger with an intake side of the compression mechanism; an intermediate heat exchanger return tube arranged and configured to connect the other end of the intermediate heat exchanger with a portion between the usage-side heat exchanger and the heat source-side heat exchanger; and an intermediate heat exchanger bypass tube connected to the intermediate refrigerant tube so as to bypass the intermediate heat exchanger, the intermediate heat exchanger having an intermediate refrigerant tube arranged and configured to draw refrigerant discharged from the first-stage compression element into the second-stage compression element.
 3. The refrigeration apparatus according to claim 2, wherein at a start of an operation, which sets the switching mechanism to the cooling operation state, the refrigerant discharged from the first-stage compression element is drawn into the second-stage compression element through the intermediate heat exchanger bypass tube, and the intermediate heat exchanger is connected with the intake side of the compression mechanism through the intake return tube.
 4. The refrigeration apparatus according to claim 2, wherein the intermediate heat exchanger return tube has a flow rate control valve.
 5. The refrigeration apparatus according to claim 1, further comprising an expansion device arranged and configured to isentropically expand refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger, the expansion device being connected to a portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit, and the rectifier circuit being arranged and configured to rectify refrigerant flow so that refrigerant flows in from an inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.
 6. The air-conditioning apparatus according to claim 5, further comprising a gas-liquid separator arranged and configured to perform gas-liquid separation of refrigerant, the gas-liquid separator being connected to an outlet of the expansion device; and a second-stage injection tube arranged and configured to return to the second-stage compression element gas refrigerant separated in the gas-liquid separator, the second-stage injection tube being connected to the gas-liquid separator.
 7. The refrigeration apparatus according to claim 3, wherein the intermediate heat exchanger return tube has a flow rate control valve.
 8. The refrigeration apparatus according to claim 7, further comprising an expansion device arranged and configured to isentropically expand refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger, the expansion device being connected to the portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit, and the rectifier circuit being arranged and configured to rectify refrigerant flow so that refrigerant flows in from an inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.
 9. The air-conditioning apparatus according to claim 8, further comprising a gas-liquid separator arranged and configured to perform gas-liquid separation of refrigerant, the gas-liquid separator being connected to an outlet of the expansion device; and a second-stage injection tube arranged and configured to return to the second-stage compression element gas refrigerant separated in the gas-liquid separator, the second-stage injection tube being connected to the gas-liquid separator.
 10. The refrigeration apparatus according to claim 3, further comprising an expansion device arranged and configured to isentropically expand refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger, the expansion device being connected to the portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit, and the rectifier circuit being arranged and configured to rectify refrigerant flow so that refrigerant flows in from an inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.
 11. The air-conditioning apparatus according to claim 10, further comprising a gas-liquid separator arranged and configured to perform gas-liquid separation of refrigerant, the gas-liquid separator being connected to an outlet of the expansion device; and a second-stage injection tube arranged and configured to return to the second-stage compression element gas refrigerant separated in the gas-liquid separator, the second-stage injection tube being connected to the gas-liquid separator.
 12. The refrigeration apparatus according to claim 4, further comprising an expansion device arranged and configured to isentropically expand refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger, the expansion device being connected to the portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit, and the rectifier circuit being arranged and configured to rectify refrigerant flow so that refrigerant flows in from an inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.
 13. The air-conditioning apparatus according to claim 12, further comprising a gas-liquid separator arranged and configured to perform gas-liquid separation of refrigerant, the gas-liquid separator being connected to an outlet of the expansion device; and a second-stage injection tube arranged and configured to return to the second-stage compression element gas refrigerant separated in the gas-liquid separator, the second-stage injection tube being connected to the gas-liquid separator.
 14. The refrigeration apparatus according to claim 2, further comprising an expansion device arranged and configured to isentropically expand refrigerant flowing between the heat source-side heat exchanger and the usage-side heat exchanger, the expansion device being connected to the portion between the heat source-side heat exchanger and the usage-side heat exchanger via a rectifier circuit, and the rectifier circuit being arranged and configured to rectify refrigerant flow so that refrigerant flows in from an inlet of the expansion device both in cases in which refrigerant flows from the heat source-side heat exchanger to the usage-side heat exchanger and cases in which refrigerant flows from the usage-side heat exchanger to the heat source-side heat exchanger.
 15. The air-conditioning apparatus according to claim 14, further comprising a gas-liquid separator arranged and configured to perform gas-liquid separation of refrigerant, the gas-liquid separator being connected to an outlet of the expansion device; and a second-stage injection tube arranged and configured to return to the second-stage compression element gas refrigerant separated in the gas-liquid separator, the second-stage injection tube being connected to the gas-liquid separator. 